CN100520099C - Connection structure of automatic transmission - Google Patents
Connection structure of automatic transmission Download PDFInfo
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- CN100520099C CN100520099C CNB2006800148905A CN200680014890A CN100520099C CN 100520099 C CN100520099 C CN 100520099C CN B2006800148905 A CNB2006800148905 A CN B2006800148905A CN 200680014890 A CN200680014890 A CN 200680014890A CN 100520099 C CN100520099 C CN 100520099C
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- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Structure Of Transmissions (AREA)
- General Details Of Gearings (AREA)
Abstract
A connection structure of an automatic transmission capable of solving a problem in a conventional connection structure wherein when the drum of a clutch is connected to the specified rotating element (ring gear) of a planetary gear by welding, the accuracy of the connection structure is lowered by the effect of heat. The flange part 25c of a drum member 25 is fixed to the outer diameter part 26b of a base member 26 by press-fitting. The fitted surface of the base member 26 forms press-fitted parts 26d1 and 26d3 at the axial both end parts and a small diameter recessed part 26d2 at the center part. The connection part 26e of the base member is spline-engaged with the ring gear R1 and locked by a snapring 28. The claw of the snapring extending in the radial outside direction is handled through a cutout part in the annular portion 62 of the ring gear.
Description
Technical field
The present invention relates in the automatic transmission on being loaded into automobile etc., predetermined rotatable member such as planetary gear ring and will rouse member and the linkage structure of these two adjacent members of drum that substructure member is fixed as one.
Background technique
In the past, clutch (or braking) drums that use in automatic transmission more, this clutch (or braking) drum has drum as follows: the inner peripheral surface that will be roused member by the clutch (and/or braking) that pressure-formed cylinder element constitutes is embedded in outward on the substructure member that is made of cylinder element, and from the outside with welding chimeric surfaces (for example, Japanese kokai publication sho 61-48616 communique) such as electron beams.
In addition, in automatic transmission, also use following linkage structure: and distributing planetary gear adjacent with above-mentioned clutch drum, fixing this planetary predetermined rotatable member of one, for example gear ring (for example, Japanese Unexamined Patent Application Publication 2005-527744 communique) on above-mentioned clutch drum.
Summary of the invention
Above-mentioned linkage structure generally is made of welded structure, the influence of heat when therefore being subjected to welding, and predetermined rotatable member such as gear ring makes the precision reduction because distortion waits, and might produce the problem of the durability reduction etc. of gear noiose and gear.
In addition, above-mentioned clutch (or braking) drum member makes a plurality of friction plate splines engagings and has predetermined length vertically, and according to the engaging of above-mentioned friction plate etc. and on above-mentioned chimeric surface the big bending moment (jam power) of effect.Therefore, above-mentioned bending moment is concentrated and is acted on welding portion, thereby constitutes weld part and heat affected zone disadvantageous structure on intensity.
In addition,, be pressed into this lip part at the outer circumferential face of substructure member though can consider to form the lip part of the boss shape that extends vertically in the interior circumferential portion of above-mentioned bulging member, and the fore-end of weld flange portion, it is big to be pressed into area, and it is big that loading of pressing in becomes.
In order to reduce this loading of pressing in and to make the assembling facilitation, consider the chimeric surface of above-mentioned substructure member is only made its fore-end as being pressed into size, other parts being constructed as the band step of summary minor diameter, only the fore-end of lip part is pressed in the substructure member and positions, in the full week of weld flange portion front end and substructure member front end under this state, drum member one is fixed on the substructure member.
Structure with the fitting surface that constitutes by the band step, between the inner peripheral surface of the minor diameter part outer circumferential face of substructure member and lip part, produce narrow gap, in manufacturing process, invade this gap as if slag inclusion, because narrow gaps, even can not remove above-mentioned slag inclusion by washing process, under such state, form friction apply device and be assembled in the automatic transmission, above-mentioned slag inclusion is emitted from the gap in automatic transmission work, and the possibility that produces the automatic transmission problem because of this slag inclusion is arranged.
The linkage structure that the purpose of this invention is to provide a kind of automatic transmission that addresses the above problem, this linkage structure is one fixing drum member and substructure member by being pressed into, and with spline with trip ring and one is connected this drum and planetary predetermined rotatable member.
The invention reside in the linkage structure of automatic transmission, it is characterized in that,
This linkage structure comprises:
The cross section is the bulging member 25 of コ word shape, outer diameter part 25b that it has bottom 25a, extend vertically from the outside diameter of this bottom and the lip part 25c that extends vertically from the internal side diameter of above-mentioned bottom;
The gear ring R1 of planetary pinion DP, its end at inner peripheral surface has spline hs and annular recess 63,
Be pressed on the outer diameter part 26b outer circumferential face of above-mentioned substructure member 26 one by lip part 25c inner peripheral surface and fix and constitute drum 20 above-mentioned bulging member 25,
The spline 61 that forms on the outer circumferential face of the joint 26e that makes at above-mentioned substructure member 26 engages with the spline hs of above-mentioned gear ring R1, and trip ring 28 is engaged with above-mentioned annular recess 63, thereby blocks above-mentioned spline 61.
According to said structure, thereby the one constant cross-section is the bulging member and the substructure member formation drum of コ word shape by being pressed into, be connected this drum and planetary gear ring with trip ring with spline, so can reduce the heat affecting that welding causes, improve the precision of gear ring and drum, prevent the generation of noise, and can improve the life-span.
Below, represent desirable form.
The annulus with above-mentioned annular recess 63 62 of above-mentioned gear ring R1 has notch 62a, 62b at least one position in full week,
Above-mentioned trip ring 28 has pawl 28a, the 28b that extends along the external diameter direction at the two ends of C shape,
Make above-mentioned pawl 28a be positioned at above-mentioned notch 62a,, above-mentioned trip ring 28 is engaged with above-mentioned annular recess 63 or break away from by operating above-mentioned pawl 28a from the external diameter direction of this notch.
Therefore, pawl from the notch operation of annulus is extended along the external diameter direction of trip ring carries out the engaging or the disengaging of 28 pairs of annular recessed portion of trip ring, so the axial space that does not need the operation aperture ring to use, can can seek the miniaturization of automatic transmission near axial arrangement every trade star gear and drum.
Above-mentioned trip ring 28 is adjacent with above-mentioned pawl 28a and have recess 28d, and the part b that this recess is used to prevent and face the above-mentioned notch 62a of above-mentioned annulus 62 interferes.
Therefore, an annulus has notch, and one side prevents that with recess notch end face and pawl adjacent portions from interfering, and prevents that claw portion from climbing up the notch end face and making the power effect of trip ring undergauge (diameter reduction) direction.
The above-mentioned notch 62a, the 62b that form at above-mentioned annulus 62 have two at least,
Operate the pawl 28a of above-mentioned trip ring 28 with an above-mentioned notch 62a, and confirm that with another above-mentioned notch 62b above-mentioned trip ring 28 is embedded into the situation in the above-mentioned annular recess 63.
Therefore, owing to have the notch of two annulus at least, carry out the undergauge operation of trip ring with a notch, carry out trip ring with another notch simultaneously and take industry really as, so can easily and carry out engaging, the disengaging operation of trip ring reliably to the annular recess embedding.
Set the axial two end part 26d of chimeric surface 26d of the lip part 25c inner peripheral surface of the outer diameter part 26b outer circumferential face of above-mentioned substructure member 26 and above-mentioned bulging member
1, 26d
3For being pressed into size, the while is part 26d therebetween
2Form the gap.
Therefore, the drum member is except the outer diameter part that the spline that engages friction plate is arranged, form the lip part that extends vertically at internal side diameter, make the outer diameter part outer circumferential face of this lip part and substructure member chimeric, and at this chimeric surface, axial two end part are to be pressed into size, and part forms the gap between it, even so because the engaging friction plate produces big bending moment with big pressing force on the drum member, two end portions by above-mentioned lip part is pressed into and is bearing on the substructure member, the drum member is bearing on the substructure member with stable high supporting precision, successfully keeps the motion of friction plate, continuously the performance of long term maintenance friction apply device.
When the substructure member outer diameter part is pressed into bulging member lip part, becoming what be pressed into size is the two end part of leaving vertically, seek alleviating of loading of pressing in, assembling easily, the gap of intermediate portion is with being pressed into portion its both sides of obturation simultaneously, even slag inclusion is invaded, can not discharge this slag inclusion after the automatic transmission assembling, can not produce the problem that causes by this slag inclusion.
Make the end of lip part 25c of the end of outer diameter part 26b of above-mentioned substructure member and above-mentioned bulging member consistent, an end of these outer diameter parts and lip part is welded together.
Therefore, the lip part that will rouse member with the pressing part that leaves vertically is bearing on the substructure member, so can prevent based on from the load concentration of the macrobending moment of drum member on the weld part of drum member and substructure member, can prevent degradation under the durability of weld part and heat affected zone.
Above-mentioned bulging member 25 is made of the one part that forms by pressure forming,
Axial two end portions at the chimeric surface 26d of the outer diameter part 26b of above-mentioned substructure member 26 outer circumferential face forms by being pressed into the 26d of the portion that is pressed into that size constitutes
1, 26d
3, form diameter at these intermediate portions that are pressed into portion and be pressed into the little recess 26d of portion than this
2
Therefore, the drum member can be with the easily and at an easy rate manufacturing of pressure-formed one-piece parts, in the outer diameter part formation of substructure member by being pressed into the portion that is pressed into and the recess that size constitutes, so easy to manufacture.
Internal side diameter at the outer diameter part 25b of above-mentioned bulging member 25 sets clutch spider hub 21,
A plurality of friction plates 22,23 of engaging ground configuration alternately between the spline 25d that the inner peripheral surface of the outer diameter part 25b of spline 21d that the outer circumferential face of the outer diameter part 21b of this clutch spider hub forms and above-mentioned bulging member 25 forms.
Therefore, clutch spider hub is set, clutch drum uses above-mentioned drum, so though big bending moment acts on the bulging member, energy is the precision and the intensity of long term maintenance clutch drum continuously.
Rise part 26a with above-mentioned substructure member 26 is the cylinder bottom surface, outer circumferential face with the boss 26c of the outer circumferential face of the lip part 25c of above-mentioned bulging member 25 and above-mentioned substructure member 26 is a slip surface, piston component 43 is embedded in above-mentioned drum 20 to seal oil tight mode, constitutes the oil pressure servomechanism installation A that above-mentioned a plurality of friction plate is used.
Therefore; when drum is constituted the oil pressure servomechanism installation as the cylinder fitting piston, serve as the outer circumferential face of drum member lip part with the outside diameter slip surface of piston component, so can guarantee that the compression area of piston is big; give the big engaging power of friction plate, can stablize, carry out reliably the action of friction apply device.
Above-mentioned piston component 43 has the piston portion 43a that constitutes above-mentioned oil pressure servomechanism installation A, the 43c of piston rod portion that extends from this piston portion along outside diameter and from the outside diameter of the above-mentioned piston portion cylindrical part 43b that extends of piston back side vertically,
Dispose releasing sheet 49 to seal oil-proof and to prevent along the mode that the boss part 26c of above-mentioned seat member 26 extracts at above-mentioned cylindrical part 43b, form at the back side of above-mentioned piston portion 43a and remove grease chamber 51.
Therefore, outside diameter at piston portion is provided with piston rod, and with the elimination sheet that is provided with continuously in cylindrical part and boss part, eliminate the grease chamber in the configuration of piston portion back side, because the outside diameter in piston portion and elimination grease chamber is prepared a plurality of friction plates of operating with piston rod, so can particularly constitute the friction apply device that comprise the oil pressure servomechanism installation compactly on axially compact ground.
The rise part 26a of above-mentioned substructure member 26 makes internal side diameter b
2Than outside diameter b
1Wall thickness (b
1＜b
2).
Therefore, the rise part of substructure member is because internal side diameter is than outside diameter wall thickness, so constitute relatively from the thrust of the predetermined rotatable member effect of gear ring etc. with from the pressing force of drum member effect and firm structure.
Reference character in the above-mentioned bracket and accompanying drawing contrast usefulness, the structure that claims are put down in writing shows no sign of influence.
Description of drawings
Fig. 1 is the skeleton diagram that expression is suitable for automatic transmission of the present invention.
Fig. 2 is the action schedule of above-mentioned automatic transmission.
Fig. 3 is the speed line chart of above-mentioned automatic transmission.
Fig. 4 is the amplification view of the part of the above-mentioned automatic transmission of expression.
Fig. 5 is the sectional view of the linkage structure of expression clutch drum of the present invention and this drum and planetary predetermined rotatable member.
Fig. 6 is the end view drawing of state of the trip ring of the chimeric predetermined rotatable member of the present invention (gear ring) of expression.
Fig. 7 is the figure of expression trip ring of the present invention, (A) is plan view, (B) is the enlarged view of end portion (B part), (C) is the sectional view of C-C line.
Embodiment
Below, based on accompanying drawing, describe at the mode of execution that the present invention is applicable to automatic transmission, at first, illustrate based on Fig. 1 to be suitable for automatic transmission 1 of the present invention
1Schematic configuration.Be applicable to for example automatic transmission 1 of the vehicle of FR type (engine behind front wheel, rear wheel drive)
1Has the automatic transmission 1 that can be connected with not shown motor
1Input shaft 11, and axially be that the center has fluid torque converter 7 and gear 2 with this input shaft 11
1In addition, in this automatic transmission, so-called the place ahead is meant the place ahead of vehicle, that is, be the mean engine side in automatic transmission, and so-called rear is meant the rear of vehicle,, is meant output shaft (transmission shaft) side with the motor opposition side in automatic transmission that is.
Above-mentioned fluid torque converter 7 has and automatic transmission 1
1The pump impeller 7a that connects of input shaft 11 and transmit the turbine wheel 7b of the rotation of this pump impeller 7a via working fluid, this turbine wheel 7b with the above-mentioned gear 2 of above-mentioned input shaft 11 coaxial settings
1Input shaft 12 be connected.In addition, on this fluid torque converter 7, has lock-up clutch 10, if this lock-up clutch 10 is engaged then above-mentioned automatic transmission 1 with the oil pressure control of not shown hydraulic pressure control device
1The rotation of input shaft 11 be directly passed to gear 2
1 Input shaft 12.
Above-mentioned gear 2
1On input shaft 12 (and jack shaft 13), have planetary pinion (epicyclic reduction gear) DP and planetary gear unit (planetary gear set) PU.Above-mentioned planet gear D P has sun gear S1, planetary carrier CR1, gear ring R1, be so-called double pinion planetary pinion, it has and the small gear P1 of sun gear S1 engagement and the small gear P2 that meshes with gear ring R1 with intermeshing form on this planetary carrier CR1.
In addition, this planetary gear unit PU has sun gear S2, sun gear S3, planetary carrier CR2 and gear ring R3 as 4 rotatable members, be the so-called dimension Nao formula planetary pinion that draws, its on this planetary carrier CR2 with intermeshing form have with the wide gear P4 of sun gear S2 and gear ring R3 engagement, with the narrow gear PS of sun gear S3 engagement.
The sun gear S1 of above-mentioned planet gear D P is connected and fixing rotation with the guide wheel shaft 3b that one is fixed on the gearbox casing 3.In addition, above line gear rack CR1 is connected with above-mentioned input shaft 12 and becomes and (hereinafter referred to as " input rotation ") rotated in the rotation of this input shaft 12 in the same manner, and, be connected with the 4th clutch C-4 (clutch is transmitted in input).And then, gear ring R1 is in by this sun gear S1 that is fixed and this planetary carrier CR1 that imports rotation the deceleration of input rotational delay is rotated, and, be connected with the 1st clutch C-1 (slow down and transmit clutch) and the 3rd clutch C-3 (slow down and transmit clutch).
The sun gear S2 of above-mentioned planetary gear unit PU is connected with the 1st break B-1 and relative gearbox casing 3 fixing freedom, and, be connected with above-mentioned the 4th clutch C-4 and above-mentioned the 3rd clutch C-3, and can import the input rotation of above line gear rack CR1 freely via the 4th clutch C-4, import the deceleration rotation of above-mentioned gear ring R1 freely via the 3rd clutch C-3.In addition, above-mentioned sun gear S3 is connected with the 1st clutch C-1, and can freely import the deceleration rotation of above-mentioned gear ring R1.
And, above line gear rack CR2 is connected with the 2nd clutch C-2 of the rotation of input input shaft 12 via jack shaft 13, by the 2nd clutch C-2, the input rotation becomes input freely, in addition, above line gear rack CR2 is connected with the 2nd break B-2 with mono-directional overrun clutch F-1, rotates in one direction thereby can limit relative gearbox casing 3 by this mono-directional overrun clutch F-1, and freely fixes rotation by the 2nd break B-2.In addition, above-mentioned gear ring R3 is connected with the output shaft 15 that rotates to not shown driving wheel output.
Then, according to above-mentioned structure, gear 2 is described based on Fig. 1, Fig. 2, Fig. 3
1Effect.In the speed line chart that Fig. 3 represents, the longitudinal axis is represented the rotating speed of each rotatable member (each gear), the gear ratio of these rotatable members of the corresponding expression of transverse axis.In the planetary pinion DP of this speed line chart part, the longitudinal axis of laterally end (left side among Fig. 3) is corresponding to sun gear S1, and later on by the order on right side in figure, the longitudinal axis is corresponding to gear ring R1, planetary carrier CR1.And then in the part of the planetary gear unit PU of this speed line chart, the longitudinal axis of laterally end (right-hand side among Fig. 3) is corresponding to sun gear S3, and later on by the order in left side in figure, the longitudinal axis is corresponding to gear ring R3, planetary carrier CR2, sun gear S2.
For example, it is D (driving) zone, at 1 velocity shooting (1st) that advances, as Fig. 2 represents, the 1st clutch C-1 and mono-directional overrun clutch F-1 engaging, so, as Fig. 1 and Fig. 3 represent, by the sun gear S1 that is fixed with as the slow down rotation of gear ring R1 of rotation of the planetary carrier CR1 of input rotation, input to sun gear S3 via the 1st clutch C-1.In addition, the rotation of planetary carrier CR2 is limited in a direction (positive veer), that is to say, prevents the counter-rotating of planetary carrier CR2, becomes the state that is fixed.So, the deceleration rotation that inputs to sun gear S3 outputs to gear ring R3 via the planetary carrier CR2 that is fixed, thereby from the just commentaries on classics of output shaft 15 outputs as 1 velocity shooting that advances.
In addition, when engine braking (when not working), with fastening the 2nd break B-2 and fixedly planetary carrier CR2 prevent that the form of just changeing of this planetary carrier CR2 from keeping the state of above-mentioned 1 velocity shooting that advances.In addition, at this 1 velocity shooting that advances, owing to can prevent the counter-rotating of planetary carrier CR2 and it is just changeed by mono-directional overrun clutch F-1, thereby, for example can carry out the finishing of 1 velocity shooting that advances when non-running region switches to running region smoothly by the automatic engaging of mono-directional overrun engaging device F-1.
At 2 velocity shootings (2nd) that advance, represent as Fig. 2, engage the 1st clutch C-1, and fastening the 1st break B-1, so, represent that as Fig. 1 and Fig. 3 the slow down rotation of gear ring R1 of rotation inputs to sun gear S3 via the 1st clutch C-1 by the sun gear S1 that is fixed with as the planetary carrier CR1 of input rotation.In addition, the fixedly rotation of sun gear S2 of fastening by the 1st break B-1.So, planetary carrier CR2 is in the low deceleration rotation of rotating ratio sun gear S3, and the deceleration rotation that inputs to this sun gear S3 outputs to gear ring R3 via this planetary carrier CR2, thereby from the just commentaries on classics of output shaft 15 outputs as 2 velocity shootings that advance.
At 3 velocity shootings (3rd) that advance, represent that as Fig. 2 the 1st clutch C-1 and the 3rd clutch C-3 are stuck.So, represent that the slow down rotation of gear ring R1 of rotation inputs to sun gear S3 via the 1st clutch C-1 by the sun gear S1 that is fixed with as the planetary carrier CR1 of input rotation as Fig. 1 and Fig. 3.In addition, since the engaging of the 3rd break B-3, the rotation of giving sun gear S2 input gear ring R1.Promptly, owing to give the deceleration rotation of sun gear S2 and sun gear S3 input gear ring R1, so planetary gear unit PU becomes the direct coupled condition of the rotation of slowing down, the rotation former state of slowing down is exported to gear ring R3, thereby from the just commentaries on classics of output shaft 15 outputs as 3 velocity shootings that advance.
At 4 velocity shootings (4th) that advance, represent that as Fig. 2 the 1st clutch C-1 and the 4th clutch C-4 are stuck.So, represent that the slow down rotation of gear ring R1 of rotation inputs to sun gear S3 via the 1st clutch C-1 by the sun gear S1 that is fixed with as the planetary carrier CR1 of input rotation as Fig. 1 and Fig. 3.In addition, because of the engaging of the 4th break B-4, and the rotation of giving sun gear S2 input planet gear frame CR1.So, planetary carrier CR2 becomes the deceleration rotation than the higher rotation of sun gear S3, the deceleration rotation that inputs to this sun gear S3 outputs to gear ring R3 via this planetary carrier CR2, thereby from the just commentaries on classics rotation of output shaft 15 outputs as 4 velocity shootings that advance.
At 5 velocity shootings (5th) that advance, represent that as Fig. 2 the 1st clutch C-1 and the 2nd clutch C-2 are stuck.So, represent that the slow down rotation of gear ring R1 of rotation inputs to sun gear S3 via the 1st clutch C-1 by the sun gear S1 that is fixed with as the planetary carrier CR1 of input rotation as Fig. 1 and Fig. 3.In addition, because of the engaging of the 2nd break B-2, input to planetary carrier CR2 and will import rotation.So, by deceleration rotation that inputs to this sun gear S3 and the input rotation that inputs to planetary carrier CR2, become the deceleration rotation higher than above-mentioned 4 velocity shootings that advance, and to gear ring R3 output, thereby from the just commentaries on classics rotation of output shaft 15 outputs as 5 velocity shootings that advance.
At 6 velocity shootings (6th) that advance, represent that as Fig. 2 the 2nd clutch C-2 and the 4th clutch C-4 are stuck.So, represent, give the input rotation of sun gear S2 input planet gear frame CR1 because of the engaging of the 4th clutch C-4 as Fig. 1 and Fig. 3.In addition, will import rotation because of the engaging of the 2nd clutch C-2 and input to planetary carrier CR2.Promptly, input to sun gear S2 and planetary carrier CR2 owing to will import rotation, so planetary gear unit PU becomes the direct coupled condition of input rotation, former state is rotated to gear ring R3 output input, thereby from the just commentaries on classics rotation of output shaft 15 outputs as 6 velocity shootings that advance.
At 7 velocity shootings (7th) that advance, represent that as Fig. 2 the 2nd clutch C-2 and the 3rd clutch C-3 are stuck.So, represent,, input to sun gear S2 via the 3rd clutch C-3 by the sun gear S1 that is fixed with as the slow down rotation of gear ring R1 of rotation of the planetary carrier CR1 of input rotation as Fig. 1 and Fig. 3.In addition, will import rotation because of the engaging of the 2nd break B-2 and input to planetary carrier CR2.So, by deceleration rotation that inputs to this sun gear S2 and the input rotation that inputs to planetary carrier CR2, and become the speedup rotation higher a little than the input rotation, and to gear ring R3 output, thereby from the just commentaries on classics rotation of output shaft 15 outputs as 7 velocity shootings that advance.
At 8 velocity shootings (8th) that advance, represent that as Fig. 2 the 2nd clutch C-2 is stuck, the 1st break B-1 is blocked to be ended.So, represent, will import rotation because of the engaging of the 2nd clutch C-2 and input to planetary carrier CR2 as Fig. 1 and Fig. 3.In addition, because of the card of the 1st break B-1 ends, the rotation of sun gear S2 is fixed.So, because of fixing sun gear S2, the input of planetary carrier CR2 rotation becomes the speedup rotation higher than above-mentioned 7 velocity shootings that advance, and to gear ring R3 output, thereby from the just commentaries on classics rotation of output shaft 15 outputs as 8 velocity shootings that advance.
At laggard 1 velocity shooting (Rev1), represent that as Fig. 2 the 3rd clutch C-3 is stuck, the 2nd break B-2 is blocked to be ended.So, as Fig. 1 and shown in Figure 3,, input to sun gear S2 via the 3rd clutch C-3 by the sun gear S1 that is fixed with as the slow down rotation of gear ring R1 of rotation of the planetary carrier CR1 of input rotation.In addition, the card because of the 2nd break B-2 ends the fixedly rotation of planetary carrier CR2.So, the deceleration rotation that inputs to sun gear S2 is exported to gear ring R3 via the planetary carrier CR2 that is fixed, thereby from the counter-rotating rotation of output shaft 15 outputs as laggard 1 velocity shooting.
At laggard 2 velocity shootings (Rev2), represent that as Fig. 2 the 4th clutch C-4 is stuck, the 2nd break B-2 is blocked to be ended.So, as Fig. 1 and shown in Figure 3, because of the engaging of the 4th clutch C-4 is rotated to the input of sun gear S2 input planet gear frame CR1.In addition, the card because of the 2nd break B-2 ends the fixedly rotation of planetary carrier CR2.So, the input rotation that is input to sun gear S2 is exported to gear ring R3 via the planetary carrier CR that is fixed, thereby from the counter-rotating rotation of output shaft 15 outputs as laggard 2 velocity shootings.
For example, at P (parking) shelves and N (neutral gear) shelves, disconnect the 1st clutch C-1, the 2nd clutch C-2, the 3rd clutch C-3 and the 4th clutch C-4.Be to become dissengaged positions between planet gear D P and the planetary gear unit PU so, between planetary carrier CR1 and the sun gear S2, between gear ring R1 and sun gear S2 and the sun gear S3.In addition, become dissengaged positions between input shaft 12 (jack shaft 13) and the planetary carrier CR2.Therefore, the transmission of power between input shaft 12 and the planetary gear unit PU becomes dissengaged positions, and just the transmission of power of input shaft 12 and output shaft 15 becomes dissengaged positions.
Then, based on the 1st clutch C-1 of Fig. 4 detailed description as friction apply device of the present invention.As mentioned above, the 1st clutch C-1 is the multiplate clutch that the gear ring R1 of epicyclic reduction gear DP and the sun gear S3 of planetary gear unit PU (at Fig. 4 not shown in the figures) are disconnected or be connected, and have clutch drum 20, clutch spider hub 21, clutch plate (outside friction disc) 22 and clutch disk (interior friction plate) 23 between these between the bulging and clutch plate hub.
As Fig. 5 shown in detail like that, clutch drum 20 with drum member 25 and substructure member 26-body fix and form, drum member 25 is that the one-piece parts that the cross section is コ word shape constitutes by pressure forming, the outer diameter part 25b that have bottom 25a, extends from the outside diameter of this bottom to axial rearward direction and from the internal side diameter of the above-mentioned bottom lip part 25c to the axial rearward direction extension.Substructure member 26 has becomes the rise part of cylinder bottom surface 26a, at the outside diameter of this rise part the outer diameter part 26b that extends of fore-and-aft direction and the boss part 26c that rearward extends from the internal side diameter of above-mentioned rise part vertically, further, above-mentioned outer diameter part 26b has the chimeric surface 26d chimeric with above-mentioned bulging member 25 on its outer circumferential face, and has the joint 26e that extends to the external diameter direction from axial forward end.
Above-mentioned epicyclic reduction gear DP and other gears 2
1Be housed in together in the gearbox casing 3, have that sun gear S1, gear ring R1 and supporting are meshing with each other and with the 1st small gear of sun gear S1 engagement and with the planetary carrier CR1 of the 2nd small gear of gear ring R1 engagement, sun gear S1 and the guide wheel shaft 3b spline fitted that is pressed into interior week of the pump cover of above-mentioned gearbox casing 3 one.Planetary carrier CR1 one is fixed on the lip part 11a of input shaft 11, and input shaft 11 rotates on the guide wheel shaft 3b that is bearing in freely as fixed component by needle bearing 24.Gear ring R1 is engaging the joint 26e of above-mentioned substructure member within it on the tooth h of side face, and on the groove that forms on this gear ring R1 chimeric trip ring 28, and be captured between on the above-mentioned substructure member 26.And then, on the outer circumferential face of this gear ring R1, also be formed with spline 29, engage clutch plate (outside friction disc) 22 and clutch disk (interior friction plate) 32 respectively at this spline 29 with between the figure inner rotary is bearing in drum 30 on the oil pump boss part 3f freely, and constitute the 3rd clutch C-3.Spline is chimeric each other at its front end with being connected drum member 33 for above-mentioned drum 30, and links into an integrated entity in sense of rotation, and this connection drum member 33 rearward extends in the mode that covers above-mentioned the 1st clutch C-1.This drum member 33 is used rivet and is connected 35 combinations of boss member with the rear part of clutch spider hub 21 at C-1, and this its front end of connection boss member 35 usefulness is connected with the 2nd sun gear (with reference to Fig. 1).In addition, reference character 38 is mono-directional overrun clutchs that card ends the direction rotation of the planetary carrier CR2 (with reference to Fig. 1) that schemes outer planetary gear unit PU.
The outer diameter part 21b that above-mentioned clutch spider hub 21 has rise part 21a, extend to axial the place ahead from its outside diameter, the boss part 21c that extends to axial rearward direction from the rise part internal side diameter.Clutch disk 23 that mutual configuration engages with spline 21d on being formed on this outer diameter part 21b and the clutch plate 22 that engages with spline 25d on the outer diameter part 25b inner peripheral surface that is formed on above-mentioned clutch drum 20, and the trip ring 36 that ends on drum member outer diameter part 25b by card blocks the reversing sheet 34 that is configured in their front ends, and constitutes many plates wet clutch.Above-mentioned clutch spider hub boss part 21c becomes hierarchic structure, is formed with spline at its minor diameter part, with its front end and quill shaft 37 engagings that are being connected the 3rd sun gear S3 (with reference to Fig. 1).
The above-mentioned C-1 substructure member boss part 26c of clutch drum 20, be bearing in freely on the input shaft 11 by rotations such as bearing shells (bush) 39, at its axial end, between the lip part 11a of itself and above-mentioned input shaft, be provided with thrust-bearing 40, and at its axial the other end, and the stepped part a of above-mentioned clutch spider hub boss part 21c between be provided with thrust-bearing 41, thereby axially be positioned.And, at drum 20, with substructure member rise part 26a as the cylinder bottom surface, and will rouse the lip part 25c outer circumferential face of member and substructure member boss part 26c outer circumferential face as slip surface, be by O shape ring 42,42 that oily close shape is chimeric piston component 43, and constitute the C-1 clutch with oil pressure servomechanism installation A.Piston component 43 comprise relative with the rise part 26a that becomes the cylinder bottom surface to piston portion 43a, the cylindrical part 43b that extends to axial front and back from the outer diameter part of this piston portion and the 43c of piston rod portion that extends to outside diameter at the front end of this cylindrical part, above-mentioned O shape ring 42,42 is entrenched in respectively and is formed at the groove on the above-mentioned cylindrical part 43b inner peripheral surface and is formed in the groove on the piston portion 43a inner peripheral surface.
Above-mentioned piston rod 43c, its front end engages with the spline 25d of C-1 clutch drum member outer diameter part 25b, and the mode with clutch drum 20 and the rotation of piston 43 one engages, in addition, the protuberance 43d that a part is outstanding in the side of this piston rod 43c across the terminal side of buffer substrate tablet 46 and each friction plate 22,21 of the 3rd clutch relative to.On the above-mentioned cylindrical part 43b of the back side of above-mentioned piston portion 43a, chimeric the sheet 49 of releasing arranged in sealed mode that can leakage of oil via O shape ring 47, this remove sheet 49 and end the trip ring 50 on substructure member boss part 26c and form between the jammed piston portion back side by card and remove grease chamber 51.Remove between the back side of sheet 49 and above-mentioned piston component 43 at this, compress in the form of a ring and be provided with a plurality of Returnning springs 48.
At above-mentioned the 1st clutch C-1, piston rod 43c erects from piston portion 43a along the external diameter direction and forms, and cylindrical part 43b is positioned at the internal side diameter of the outer diameter part 21b of clutch spider hub 21, and by this cylindrical part with remove sheet 49 and forms releasing grease chamber 51, so the outside diameter in piston portion 43a and releasing grease chamber 51 can dispose a plurality of friction plates 22,23, can particularly constitute this clutch C-1 that comprises oil pressure servomechanism installation A compactly vertically compactly.
On input shaft 11, be formed with oil circuit 52,53, supply with operating oil pressures to oil circuit 52, and the horizontal oil circuit e by input shaft 11, the annular slot f that do not leak the mode zoning of Shan with sealing with O shape ring reach the oilhole 55 that forms and offer oil pressure servomechanism installation A on substructure member boss part 26c.Press to above-mentioned oil circuit 53 supplying lubricating oils, this oil circuit 53 with and the oil circuit 57 of the jack shaft 56 that engages of input shaft 11 splines be connected, and then, emit to above-mentioned releasing grease chamber 51 from the oilhole 59 that is formed on the substructure member boss part 26c by horizontal oil circuit g, the k of grease chamber.Be formed with otch 49a at the inside diameter of removing sheet 49, make oil spill stream, and be directed to the 1st clutch C-1 from this releasing grease chamber 51.
Then, describe the linkage structure of C-1 clutch drum 20 of the present invention and this drum 20 and gear ring R in detail based on Fig. 5.As described above, clutch drum 20 is fixed drum member 25 and substructure member 26 one and is formed.The outer circumferential face of the outer diameter part 26b of substructure member 26 becomes chimeric surface 26d, this chimeric surface 26d, and central part is whittled into ring-type a little and becomes recess 26
2, both sides become by being pressed into the portion that is pressed into 26 that size constitutes before and after it
1, 26
3This substructure member chimeric surface 26d goes up chimeric the lip part 25c inner peripheral surface of drum member, but the portion that just is pressed into 26 that is pressed into and seals at this moment
1, 26
3, recess 26
2And between the inside diameter 25c inner peripheral surface some gaps are arranged.Thereby, when drum member 25 is pressed into substructure member 26, become chimeric area, but be pressed into portion 26 based on the ratio broad of drum member lip part 25c
1, 26
3Axial length (area) shorter, just can be pressed into smaller loading of pressing in.
The rise part 26a of above-mentioned substructure member 26 is formed by discoideus, but its wall thickness, internal side diameter (b
2) than outside diameter (b
1) thick (b
1＜b
2).Among Fig. 5,25e is the annular recess that engaging reversing sheet 34 is pushed the trip ring 36 of usefulness, and 26f is that the annular recess that sheet 49 is pushed the trip ring 36 of usefulness is removed in engaging, the 60th, accommodate the recess of thrust-bearing 40.
Above-mentioned clutch drum 20 and above-mentioned planet gear D P disposed adjacent, and and link into an integrated entity as the gear ring R1 of this planetary predetermined rotatable member.The tooth h of this gear ring R1 extends vertically, and the clutch drum side becomes spline hs, and the front end of the joint 26e of above-mentioned substructure member 26 forms the spline 61 that can engage with above-mentioned spline hs.
The clutch drum side of above-mentioned gear ring R1 becomes vertically outstanding annulus 62, and at the inner peripheral surface of this annulus and formation annular recess 63 adjacent with above-mentioned spline hs.Above-mentioned annulus 62 as Fig. 6 represents, is cut open at two positions, constitutes the notch 62a, the 62b that become the space that there are not this annulus.
The trip ring 28 that engages with above-mentioned annular recess 63, as Fig. 7 represented, the front saw by C shape and constitutes that there is pawl 28a, the 28a that extends along the external diameter direction at its two end part.This claw portion cuts the one side, becomes thin-walled and compare with other parts (main part) 28c, and forms recess 28d between this pawl 28a and the main part 28c.
Above-mentioned clutch drum 20, basically by on its outer diameter part chimeric surface 26, being pressed into lip part 25c inner peripheral surface, and one fixing drum member 25 and substructure member 26, the heat affecting of welding is few.And, limit the direction of rotation by the spline fitted hs, 61 of joint 26e, and pass through the engaging restrictive axes direction of 28 pairs of annular recess 63 of trip ring, thereby this clutch drum 20 and gear ring R1 are linked into an integrated entity.Therefore, the influence that is connected also the heat that not welding produces of clutch drum 20 and gear ring R1 can highi degree of accuracy be kept gear ring R1.
Above-mentioned clutch drum 20 and gear ring R1 must constitute compact structure aspect vehicle loading, and according to gap little such configuration of trying one's best, not from the space of axle direction operation aperture ring 28.Therefore, gear ring R1 forms notch 62a, 62b to the side-prominent annulus 62 of clutch drum, clamps along a pair of pawl 28a, the 28a of the outstanding trip ring 28 of external diameter direction by a notch, makes trip ring 28 undergauges.Under this state, the spline hs of engaging gear ring R1 on the spline 61 of joint 26e, and make gear ring R1 near joint 26e, trip ring 28 overlaps with annular recess 63, by removing undergauge, trip ring 28 is engaged with annular recess 63 from external diameter direction operation pawl 28a.
At this moment,, can be positioned at consistent location, can easily and carry out the engaging of trip ring 28 reliably with Visual Confirmation trip ring 28 and annular recess 63 by another otch 62b of above-mentioned annulus.The end face y that is used to prevent and face the annulus of notch 62a adjacent to the recess 28d of the pawl 28a of trip ring 28 interferes, for example, trip ring 28 and groove 63 relative rotations, even pawl 28a is connected to above-mentioned end face y, the adjacent inclined of pawl and main part 28c and with above-mentioned end face butt, do not make the power effect on the direction of trip ring 28 undergauges.
The effect of the 1st clutch C-1 (friction apply device) part of the present invention then, is described.Do not supplying with under the state of oil pressure to oil pressure servomechanism installation A, piston component 43 is owing to Returnning spring 48 is positioned at illustrated state, and the teat 43d of piston rod 43a leaves clutch plate 21,22,46, the 1 clutch C-1 and is in off state.Under this state, if supply with predetermined oil pressure to oil pressure servomechanism installation A by oil circuit 52, e, f, 55, piston component 43 is revolted Returnning springs 48 and is moved, and the teat 43d of piston rod pushes a plurality of clutch plate 22, clutch plate 23 and makes its close proximity by buffer substrate tablet 46.Therefore, the 1st clutch C-1 connects, and via clutch drum 20, above-mentioned clutch plate 22,23, clutch spider hub 21 and quill shaft 37 rotation of gear ring R1 is passed to the 3rd sun gear S3.
In addition, piston rod 43a acts on the fore-end of the outer diameter part 25b of bulging member 25 to the pressing force of clutch plate via moveing backward sheet 34 and spline 36.Therefore, the chimeric surface 26d effect bending moment (jam power) of the snap-latch surface of drum 25 pairs of conducts of member and substructure member 26 engagings, but bulging member 25 axially has the lip part 25c of predetermined length, and be pressed into and be fitted to its rear end part and be pressed into the 26d of portion
1, 26d
2So above-mentioned bending moment does not become concentrated load and disperses, can reliably support.
On the other hand, planetary pinion DP is made of spiral gear, but according to the transmission of power of this spiral gear, gear ring R1 produces the thrust to the right (direction of arrow) of Fig. 5.On the rise part 26a that the stepped part and the joint 26e of this thrust by spline hs acts on substructure member 26, but the past more internal side diameter of the rise part 26a of this substructure member 26 thick more (b of wall then
1B
2), so become the firm structure of thrust that the spiral gear of above-mentioned relatively clutch pressing force and gear ring R1 causes.Therefore, prevent weld part w concentrated load and problem such as be damaged, and drum member 25 is because by the reliable and high supporting of precision of above-mentioned substructure member 26 quilts, so even big power effect is arranged when above-mentioned clutch engages, can on a plurality of clutch plate 22,23, move smoothly, can carry out the high snap action of precision.
Further, the outside diameter of piston component 43 slides on the outer circumferential face of lip part 25c, because the correct supporting of above-mentioned clutch drum member 25, the lip part 25c that becomes above-mentioned slip surface keeps high positional accuracy, keep moving smoothly of piston component 43, and can make piston area increase the outer diameter part 26b of substructure member and the thickness degree of rousing the lip part 25c of member, can obtain big clutch pressing force.
When cutting off clutch by the oil pressure release of oil pressure servomechanism installation A, piston component 43 owing to Returnning spring 48 and the centrifugal force that acts on the oil of removing grease chamber 51 return, at this moment, piston 43 slides on the lip part 25c of above-mentioned high positional accuracy and boss part 26c smoothly, becomes the clutch off state at a gallop.
In addition, the foregoing description forms on the outer diameter part 26b of substructure member 26 outer circumferential face and is pressed into the 26d of portion
1, 26d
3And recess 26d
2, but also can on the inner peripheral surface of the lip part 25c that rouses member 25, form.In addition, be suitable for the 1st clutch C-1 as friction apply device, but also can be other clutches or break, and can be the friction apply device of other automatic transmission.In addition, the planetary predetermined element that is connected with clutch (or break) drum is a gear ring, but is not limited to this, also can be other predetermined rotatable members such as planetary carrier.
Utilizability on the industry
The syndeton of automatic transmission of the present invention, load at automobile, by engagings such as clutches The engaging of member, disengagement and change planetary power transmission line and carry out the automatic transmission of speed change In, as the predetermined spinner member of planetary gear ring etc. with bulging member and the end of clutch drum etc. The syndeton that the fixing drum of seat member one is connected and utilizing.
Claims (11)
1. the linkage structure of an automatic transmission is characterized in that, this linkage structure comprises:
The cross section is the bulging member of コ word shape, outer diameter part that it has the bottom, extend vertically from the outside diameter of this bottom and the lip part that extends vertically from the internal side diameter of above-mentioned bottom;
Substructure member, the outer diameter part that it has rise part, extend vertically from the outside diameter of this rise part, the above-mentioned boss part of extending vertically from the internal side diameter of above-mentioned rise part and the joint that extends from an end of above-mentioned outer diameter part;
Planetary gear ring, its end at inner peripheral surface has spline and annular recess,
Be pressed on the outer diameter part outer circumferential face of above-mentioned substructure member one by lip part inner peripheral surface and fix and constitute drum above-mentioned bulging member,
The spline that forms on the outer circumferential face of the joint of above-mentioned substructure member is engaged with the spline of above-mentioned gear ring, and trip ring is engaged with above-mentioned annular recess, thereby block above-mentioned spline.
2. as the linkage structure of the automatic transmission of claim 1 record, it is characterized in that,
The annulus with above-mentioned annular recess of above-mentioned gear ring has notch at least one position in full week,
Above-mentioned trip ring has the pawl that extends along the external diameter direction at the two end part of C shape,
Make above-mentioned pawl be positioned at above-mentioned notch, operate above-mentioned pawl, thereby above-mentioned trip ring is engaged with above-mentioned annular recess or break away from by external diameter direction from this notch.
3. as the linkage structure of the automatic transmission of claim 2 record, it is characterized in that,
Above-mentioned trip ring has recess adjacent to above-mentioned pawl, and the part that this recess is used to prevent and face the above-mentioned notch of above-mentioned annulus interferes.
4. as the linkage structure of claim 2 or 3 automatic transmission of putting down in writing, it is characterized in that,
The above-mentioned notch that forms on above-mentioned annulus has two at least,
Operate the pawl of above-mentioned trip ring by an above-mentioned notch, and confirm that by another above-mentioned notch above-mentioned trip ring is embedded into the situation in the above-mentioned annular recess.
5. as the linkage structure of the automatic transmission of claim 1 record, it is characterized in that,
The axial two end portions of chimeric surface of lip part inner peripheral surface tabling of setting the outer diameter part outer circumferential face of above-mentioned substructure member and above-mentioned bulging member is for being pressed into size, and the part between this two end portions forms the gap.
6. as the linkage structure of the automatic transmission of claim 1 record, it is characterized in that,
Make an end of end of above-mentioned substructure member outer diameter part and above-mentioned bulging member lip part consistent, and an end of these outer diameter parts and lip part is welded together.
7. as the linkage structure of claim 5 or 6 automatic transmission of putting down in writing, it is characterized in that,
Above-mentioned bulging member is made of the one part that forms based on pressure forming,
Form by being pressed into the portion that is pressed into that size constitutes in the axial two end portions of the chimeric surface of the outer diameter part outer circumferential face of above-mentioned substructure member, be pressed into part between the portion at these and form diameters and be pressed into the little recess of portion than this.
8. as the linkage structure of the automatic transmission of claim 1 record, it is characterized in that,
Internal side diameter at the outer diameter part of above-mentioned bulging member sets clutch spider hub,
Dispose a plurality of friction plates in the mode that alternately engages between the spline that on the spline that forms on the outer circumferential face of the outer diameter part of this clutch spider hub and inner peripheral surface, forms at the outer diameter part of above-mentioned bulging member.
9. as the linkage structure of the automatic transmission of claim 8 record, it is characterized in that,
Rise part with above-mentioned substructure member is the cylinder bottom surface, outer circumferential face with the boss part of the outer circumferential face of the lip part of above-mentioned bulging member and above-mentioned substructure member is a slip surface, piston component is embedded in above-mentioned drum to seal oil tight mode, constitutes the oil pressure servomechanism installation that above-mentioned a plurality of friction plate is used.
10. as the linkage structure of the automatic transmission of claim 9 record, it is characterized in that,
Above-mentioned piston component has the piston portion that constitutes above-mentioned oil pressure servomechanism installation, the piston rod portion of extending from this piston portion along outside diameter and from the outside diameter of the above-mentioned piston portion piston back side cylindrical part of extending vertically,
Dispose the releasing sheet in above-mentioned cylindrical part to seal mode oil-proof and that block the boss part of above-mentioned substructure member, form at the back side of above-mentioned piston portion and remove the grease chamber.
11. the linkage structure as the automatic transmission of claim 1 record is characterized in that,
The rise part of above-mentioned substructure member makes internal side diameter than outside diameter wall thickness.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP148745/2005 | 2005-05-20 | ||
| JP2005148745 | 2005-05-20 | ||
| JP332099/2005 | 2005-11-16 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101171436A CN101171436A (en) | 2008-04-30 |
| CN100520099C true CN100520099C (en) | 2009-07-29 |
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ID=39391370
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006800148905A Expired - Fee Related CN100520099C (en) | 2005-05-20 | 2006-04-21 | Connection structure of automatic transmission |
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| CN (1) | CN100520099C (en) |
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| US8664938B2 (en) * | 2010-05-05 | 2014-03-04 | Ysi Incorporated | Replaceable probe head |
| CN104088922A (en) * | 2013-04-01 | 2014-10-08 | 内蒙古欧意德发动机有限公司 | Clutch gear hub and machining method thereof |
| JP6802120B2 (en) * | 2017-07-26 | 2020-12-16 | 株式会社エクセディ | Clutch release device |
| JP2020143760A (en) * | 2019-03-08 | 2020-09-10 | 本田技研工業株式会社 | Multi-plate friction clutch |
| CN113048229B (en) * | 2021-03-08 | 2023-09-22 | 泰安东升服装有限公司 | Planet positioning fastener for clothing production |
| CN114083969B (en) * | 2021-10-29 | 2024-06-14 | 如果科技有限公司 | Dual-motor drive axle assembly and vehicle |
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