JPH09196148A - Twin clutch type transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a twin-clutch type transmission in which sufficient lubrication oil is stored between relatively rotated members to perform the sufficient lubrication, and no wear or seizure is generated. SOLUTION: A through groove 51 is formed in a surface of a thrust washer 31 to be arranged between a first clutch output disk 12 and a second clutch output disk 22 on the side of the second clutch output disk 22, and a non-through groove 61 is formed in a surface on the first clutch output disk 12. A claw 41 of the thrust washer 31 is loosely engaged with a hole 22a provided in the second clutch output disk 22, a clearance L2 on the inner circumferential side between the hole 22a and the claw 41 is larger than a clearance L2 on the outer circumferential side, the lubricating oil reached an oil chamber 122 flows more between the thrust washer 31 and the first output disk 12 than between the thrust washer 31 and the second clutch output disk 22, and the lubricating oil is stored in the non-through groove 61.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a twin clutch type transmission, and more particularly to a structure of a clutch portion thereof.

[0002]

2. Description of the Related Art A first clutch for connecting and disconnecting an input shaft and a first speed change mechanism having a first speed ratio, and an input shaft and a second speed ratio which are arranged coaxially adjacent to the first clutch. A twin clutch type transmission that has a second clutch that connects and disconnects a second speed change mechanism that is provided and that achieves a plurality of shift speeds by controlling the connection and disconnection of the first clutch and the second clutch is known. A person also applied for a twin clutch type transmission as described above in Japanese Patent Application No. 7-188907.

[0003]

In the twin clutch type transmission, the member of the first clutch and the member of the second clutch that rotates relatively to the member of the first clutch are arranged adjacent to each other. For example, in the device of the above application,
Since the output disc of the first clutch and the output disc of the second clutch are arranged adjacent to each other and rotate relative to each other, a thrust washer is disposed between the output disc of the first clutch and the output disc of the second clutch, and the thrust washer is placed between both members. To reduce friction. However, this thrust washer is engaged with the output disc of the second clutch in a non-rotatable manner, and relative rotation occurs between the thrust washer and the output disc of the first clutch. There was a possibility that sufficient lubricating oil would not be accumulated during the period, sufficient lubrication could not be performed, and wear and seizure might occur (see FIGS. 13, 14 and 15).

In view of the above problems, it is an object of the present invention to provide a twin clutch type transmission in which lubricating oil is sufficiently stored between members that rotate relative to each other and sufficient lubrication is performed to prevent wear and seizure. .

[0005]

According to the invention of claim 1, a first clutch for connecting and disconnecting an input shaft and a first speed change mechanism having a first speed ratio, and a first clutch which is coaxially adjacent to the first clutch. A second clutch that connects and disconnects the input shaft and a second speed change mechanism having a second speed ratio, and achieves a plurality of shift speeds by controlling the connection and disconnection of the first clutch and the second clutch. In the twin clutch type transmission,
A friction reducing member is interposed between the member of the clutch and the member of the second clutch that faces the member of the first clutch in the axial direction and rotates relative to the member of the first clutch. The two clutch members are non-rotatably coupled to one of the members, and extend through the surface on the opposite side of the friction reducing member from the inner diameter side end portion toward the outer diameter side end portion. There is provided a twin clutch type transmission characterized in that a concave portion is formed and an oil passage communicating with the concave portion is formed to guide the lubricating oil to the concave portion so that the lubricating oil is collected in the concave portion.

In the twin-clutch transmission having such a structure, the lubricating oil is sufficiently accumulated in the recess to improve the lubrication, and the first clutch member and the first clutch member face each other in the axial direction. Thus, friction between the members of the second clutch that relatively rotate is reduced.

According to a second aspect of the invention, in the first aspect of the invention, the outer diameter of the recess is set to one of the first clutch member and the second clutch member to which the friction reducing member is coupled. There is provided a twin clutch type transmission in which the inner diameter of a portion of the member extending in the axial direction on which the centrifugal oil pressure of the lubricating oil acts is larger than the inner diameter. In the twin clutch type transmission configured as described above, since the hydraulic pressure of the lubricating oil accumulated in the recess is increased by the centrifugal force, the first clutch member and the second clutch
The centrifugal oil pressure of the lubricating oil acts on the portion of one of the clutch members extending in the axial direction to cancel the attempt to bring the first clutch member and the second clutch member closer to each other. it can.

[0008]

Embodiments of the present invention will be described below with reference to the accompanying drawings. FIG. 1 is a skeleton diagram showing the structure of a twin clutch type automatic transmission to which the present invention is applied. Referring to FIG. 1, an input shaft 10 connected to an output shaft of an engine (not shown) includes a first clutch input disk 11 of a first clutch C1 and a second clutch C2 of a second clutch C2 that form a clutch C. The input disk 21 is connected. Engagement and release of the first clutch C1 and the second clutch C2 are performed by controlling the hydraulic pressure supplied by a hydraulic pressure supply control device (not shown).

The first clutch output disc 12 of the first clutch C1 and the second clutch output disc 22 of the second clutch C2 are respectively attached to the first clutch output shaft 1
The third and second clutch output shafts 23 are coaxially connected to the outside of the input shaft 10. The auxiliary shaft X _S and the output shaft X _{o of} the transmission mechanism are arranged parallel to these shafts.

A clutch C is attached to the first clutch output shaft 13.
From the side of, a sub-shaft drive gear I _S , a fifth speed drive gear I ₅ , and a third speed drive gear I ₃ are arranged, and further, a third speed drive gear I _S.
The third synchronizer D3 is disposed between speed drive gear I ₃ and the fifth speed drive gear I _5. Countershaft drive gear I
_S is fixedly connected to the first clutch output shaft 13 and always rotates integrally with the first clutch output shaft 13, but the third speed drive gear I ₃ and the fifth speed drive gear I ₅ are rotatably attached. The third synchronizer D3 selectively connects the first clutch output shaft 13 as described below.

The third synchronizer D3 has a first clutch output shaft 1
Third hub H3 fixedly connected to the third hub S3 and a third sleeve S3 axially slidably mounted on the outer peripheral end thereof.
Consists of This third unillustrated sleeve S3 means to move through the third shift fork Y3, third speed drive gear I ₃ to the fixing coupled with and third speed clutch gear G _3, or the fifth speed drive gear I _By engaging the fifth speed clutch gear G ₅ fixedly connected to ₅ , the third speed drive gear I ₃ and the fifth speed drive gear I ₅ are connected to the first clutch output shaft 13.

A second speed drive gear I ₂ and a fourth speed drive gear I ₄ are fixedly connected to the second clutch output shaft 23. The output shaft X _O, from the side of the clutch C, the fifth speed drive gear I ₅ and the fifth speed driven gear O ₅ which meshes at all times, the third speed driven gear O ₃ which always meshes with the third speed drive gear I _3, the 4th speed driven gear O ₄ and 2nd speed drive gear I ₂ which always mesh with 4th speed drive gear I _4.
A second speed driven gear O ₂ is provided which constantly meshes with the fourth speed driven gear O ₄ and the second speed driven gear O _2.
A first synchronizer D1 is arranged between them. Of these,
Fifth speed driven gear O _5, third speed driven gear O ₃ is fixedly connected to the output shaft X _O, but rotates in the continuous output shaft X _O integrally with the fourth speed driven gear O _4, the second speed driven gear O ₂ is attached rotatably, it is selectively connected to the output shaft X _O as shown below by the first synchronizer D1.

The first synchronizer D1 comprises a first hub H1 fixedly connected to the output shaft X _O and a first sleeve S1 axially slidably mounted on its outer peripheral end. The first sleeve S1 is moved via the first shift fork Y1 by means (not shown), and the fourth speed driven gear O
Fourth speed is fixedly coupled to the _fourth clutch gear G _4, or a is fixedly coupled to the second speed driven gear O ₂ 2
The fourth speed driven gear O ₄ and the second speed driven gear O ₂ are connected to the output shaft X _O by engaging the high speed clutch gear G ₂ .

Secondary axis X_SFrom the clutch C side,
Drive gear I_SDriven gear that always meshes with
O_S, 4th speed drive gear I_FourFirst gear that always meshes with
Live gear i₁, 2nd speed drive gear I_TwoAlways mesh with
Reverse drive gear I_RIs installed, and
Live gear i₁And reverse drive gear I_RSecond synchronization during
Device D2 is provided. Of these, the sub-axis driven gear
O_SIs the minor axis X_SIt is fixedly connected to the_SAnd one
It rotates around the body, but the first speed drive gear I₁And reverse drive
Bugia I_RIs rotatably mounted and has a second synchronization
Output shaft X is selectively selected by device D2 as follows. _OLinked to
Is done.

The second synchronizer D2 comprises a second hub H2 fixedly connected to the counter shaft X _S and a second sleeve S2 axially slidably mounted on its outer peripheral end. This second sleeve S2 is moved via the second shift fork Y2 by means (not shown), and the first speed drive gear I ₁
The first speed drive gear I ₁ and the reverse driven gear I _R are engaged by engaging the first speed clutch gear G ₁ attached to the vehicle or the reverse drive clutch I _R fixedly coupled to the reverse drive gear I _R. Is rotated integrally with the sub-axis X _S.

Here, the first speed clutch gear G ₁ is attached to the first speed drive gear I ₁ via the one-way clutch F, and the inner side (inner race) connected to the second synchronizer D 1 is It engages only when it rotates faster than the outside (outer race) connected to the first speed drive gear I ₁ , and does not engage in the opposite case.

M _R is an idler gear for reverse gear,
This is for always meshing with both the reverse drive gear I _R and the second speed drive gear I ₂ so that the reverse drive gear I _R can be connected to the second speed driven gear O ₂ when the reverse speed is selected. However, if it is possible to directly mesh the reverse drive gear I _R with the second speed driven gear O ₂ , including the gear ratio and the like, it is possible to remove it.

Next, FIG. 2 shows a first clutch C for obtaining each speed in the first embodiment configured as described above.
1 shows the combination of engagement of the first and second clutches C2, the first sleeve S1, the second sleeve S2, and the third sleeve S3, and the operating state of the one-way clutch F. In the figure, the circle marks indicate that they are engaged, but here, in the columns of the first sleeve S1, the second sleeve S2, and the third sleeve S3, 2 and N and 4, 1 and R, and 3 and N, respectively. And 5, but this is, for example, the first sleeve S1.
If there is ○ at the 2, the first sleeve S1 moves to the side of the second speed driven gear O _2, the second speed driven gear O ₂ indicate that allowed to connected to the output shaft X _O, at the 4 ○ if there is, the first sleeve S1 moves to the side of the fourth speed driven gear O _4, a fourth speed driven gear O ₄ indicates that allowed to connected to the output shaft X _O, in the neutral position if there is ○ at the N That is, none of the driven gears is connected to the output shaft X _O. In the column of the one-way clutch F, a circle indicates that the transmission action is performed, and a blank mark indicates that the transmission action is not performed by idling.

As shown in FIG. 2, for example, the first speed is
The first clutch C1 engaged, the first sleeve S1 moves to the side of the second speed driven gear O _2, to move the second sleeve S2 to the first speed side of the drive gear I _1, the third sleeve S3
Is achieved by setting the neutral position to engage the one-way clutch F and establish the following transmission path.

First torque transmission path (only symbols): 10 → 11 → 12 → 13 → I _S → O _S → X _S → H2 → S
2 → G ₁ → F → I ₁ → I ₄ → 23 → I ₂ → O ₂ → G ₂ →
S1 → H1 → X _O

FIG. 3 is a sectional view of a portion of the clutch C.
In FIG. 3, the clutch housing 1 is axially connected to the mission housing 2 on the outer peripheral side, and the input shaft supporting portion 3 is formed on the inner peripheral side. An input shaft 10 is rotatably engaged with the input shaft support portion 3. Reference numeral 4 is a seal ring that seals the hydraulic oil and the lubricating oil. A second clutch output shaft 23 rotatably supported by the input shaft 10 is provided outside the input shaft 10, and a second clutch output shaft 23 is rotatably supported outside the second clutch output shaft 23. A first clutch output shaft 13 is arranged.

The first clutch C1 is a first clutch input disk 11 welded to the input shaft 10, a first clutch / clutch plate 14 and a first clutch output shaft 13 splined to the first clutch input disk 11. First clutch output disc 12 splined to
Is spline-coupled to the first clutch output disk 12, and the first clutch piston 15 causes the first clutch
It comprises a first clutch / clutch disc 16 which is selectively frictionally engaged with the clutch plate 14.

The first clutch piston 15 is constantly urged toward the disengagement side by the first clutch spring 17, but the first oil groove 3a of the input shaft support portion 3 and the oil passage 10a of the input shaft 10 are provided.
When hydraulic oil is supplied to the first clutch piston oil chamber 115 through the passage and a pressing force that overcomes the urging force of the first clutch spring 17 is applied, it moves to the right in the figure and moves to the first clutch / clutch plate 14. The first clutch / clutch disc 16 is frictionally engaged.

On the other hand, the second clutch C2 is a second clutch input disk 21 welded to an intermediate hub 28 splined to the input shaft 10, and a second clutch input disk 21 to be splined to the second clutch input disk 21. A clutch plate 24, a second clutch output disk 22 splined to the second clutch output shaft 23, and a splined connection to the second clutch output disk 22, and selectively to the second clutch / clutch plate 24 by a second clutch piston 25. A second clutch / clutch disc 26 which is frictionally engaged with.

The second clutch piston 25 is constantly urged toward the disengagement side by the second clutch spring 27, but the second oil groove 3b of the input shaft support portion 3 and the oil passage 10c of the input shaft 10 are provided.
When the hydraulic oil is supplied to the second clutch piston oil chamber 125 through the passage and a pressing force that overcomes the urging force of the second clutch spring 27 is applied, the hydraulic oil moves to the right in the drawing and moves to the second clutch / clutch plate 24. The second clutch / clutch disk 26 is frictionally engaged.

The second clutch input disk 21 of the second clutch C2 also serves as a support member for the first clutch spring 16 of the first clutch C1.
1 does not have a special spring supporting member, but the second clutch C2 cannot separately support the second clutch spring 27, so that the second clutch spring supporting disk 29 is separately provided. It is arranged.

A lip seal 5a arranged between the first clutch input disc 11 and the first clutch piston 15 and a lip seal 5b arranged between the second clutch input disc 21 and the second clutch piston 25. Are lip seals arranged between the first clutch piston 15 and the second clutch input disc 21 to prevent leakage of hydraulic oil in the first clutch piston oil chamber 115 and the second clutch piston oil chamber 125, respectively. 5c, the lip seal 5d disposed between the second clutch piston 25 and the second clutch spring support disk 29 is the lip seal 5d.
Oil is secured in the space formed by the above, the centrifugal oil pressure acting on the second clutch piston 25 is canceled, and the oil introduced into the thrust washer portion described later is secured.

Since the first clutch input disk 11 and the second clutch input disk 21 rotate relative to each other, a thrust washer is arranged between them in order to prevent direct contact between them and allow them to rotate smoothly. The present invention relates to the structure of this thrust washer.

FIG. 4 is an enlarged sectional view showing a portion of the thrust washer 31 of the first embodiment, and FIG. 5 is a view showing a single thrust washer 31 and FIG. Is a view seen from the first clutch output disk 12 side,
(B) is a view taken along the line VV in (a) of FIG. 5, (c)
FIG. 6 is a view seen from the second clutch output disc 22 side.

As shown in FIG. 5, the thrust washer 3
Reference numeral 1 has two claws 41 projecting toward the second clutch output disc 22, and the claws 41 are engaged with holes 22 a formed in the second clutch output disc 22. Although this engagement is loose, the second clutch output disk 22 and the thrust washer 31 are prevented from rotating relative to each other, and both rotate integrally. Therefore, the thrust washer 3
The surface on the side of the first clutch output disc 12 rotates relative to the surface of the first clutch output disc 12. Therefore, the side of the first clutch output disk 12 of the thrust washer 31 is made of a copper-based first member 31A having good slippage, and the side of the second clutch output disk 22 is made of a strong iron-based second member 31B. Has been.

Here, the gap L1 between the outer peripheral side (upper side in the figure) of the claw 41 and the hole 22a is the inner peripheral side (lower side in the figure) and the hole 22.
It is smaller than the gap L2 between a. Therefore, the intermediate hub 28 passes through the third oil groove 3c formed in the input shaft support portion 3 and the third oil hole 10b formed in the input shaft 10.
Through the oil passage 28a formed in the oil chamber 1 as shown by arrow A.
The amount of the lubricating oil introduced into the first clutch output disk 12 as indicated by the arrow A2 flows in between the second clutch output disk 22 and the thrust washer as indicated by the arrow A1.
It is designed to be less than the amount flowing between the thrust washer 31 and the thrust washer 31. This is because there is no relative rotation between the second clutch output disc 22 and the thrust washer,
This is because no lubrication is required.

As in the case of the prior art shown in FIGS. 13 and 14, the gap L1 between the outer peripheral side (upper side in the figure) of the claw and the hole is set between the inner peripheral side (lower side in the figure) and the hole. If a large amount of oil is introduced between the second clutch output disc 22 and the thrust washer by making the gap smaller than the gap L2 of the first clutch output disc 12 and the thrust washer, the thrust washer is pushed toward the first clutch output disc 12 side. It will worsen the flow of lubricating oil between.

Further, in the first embodiment, the following measures are incorporated to improve the flow of the lubricating oil between the first clutch output disc 12 and the thrust washer 31. One is thrust washer 3
1 is a through groove 51 formed on the side of the second clutch output disk 22. Through the through groove 51, the escape of the lubricating oil flowing between the thrust washer 31 and the second clutch output disk 22 as shown by an arrow A3. It improves and further improves the ability to prevent the thrust washer 31 from being pushed toward the first clutch output disc 12.

The other one is the first of the thrust washers 31.
Non-penetrating groove 61 formed on the clutch output disk 12 side
The non-penetrating groove 61 forms an oil sump, and as shown by an arrow A4, the thrust washer 31 and the first
The lubricating oil that has flowed into the space between the clutch output disks 12 does not escape as it is, stays once in this oil pool, and from there, lubricates the portion where the non-penetrating groove 61 is not formed and flows to the outer peripheral side. Lubrication is improved. Further, since the throttle is inserted in the middle of the flow of the lubricating oil, the pressure of the lubricating oil is increased, and as a result, the thrust washer 30 is also pushed to the second clutch output disk 22 side, so that the thrust washer 31 And the lubrication of the first clutch output disc 12 is further improved. In FIG. 5A, the region where the oil sump is formed is shown by mesh hatching.

FIG. 6 is an enlarged sectional view of the thrust washer portion of the second embodiment. The thrust washer 32 according to the second embodiment is formed with a step so that a recess 72 spaced from the first clutch output disc 12 is formed on the inner peripheral side of the first clutch output disc 12 side. The lubricating oil is accumulated in the step portion, and as a result, the number of steps for processing the non-penetrating groove is not required as compared with the first embodiment. A through groove 52 similar to that of the first embodiment is formed on the side of the second clutch output disk 22.

Therefore, the lubricating oil flowing into the oil chamber 122 as shown by the arrow A and further flowing into the gap L1 as shown by the arrow A1 is the same as in the first embodiment.
As shown in the arrow A2,
The lubricating oil flowing into the gap L2 is indicated by arrow A
5, it flows toward the recess 72. 7A and 7B are views showing a single unit of the thrust washer 32 of the second embodiment. FIG. 7A is a view seen from the first clutch output disk side 12, and FIG. 7B is a view of FIG. ) Is a view taken along the line VII-VII in FIG. The mesh hatched portion in FIG. 7A is a region where an oil sump is formed as in FIG. 5A, and the oil sump over a much larger area than in FIG. 5A. Is clearly formed, and accordingly, it has excellent lubricity.

By the way, the second clutch output disk 22
When a portion of the lubricating oil that has flowed into the oil chamber 122 as indicated by the arrow A and flows as indicated by the arrow A0 is accumulated on the inner peripheral surface 22b of the axially extending portion, centrifugal hydraulic pressure acts. As a result, the second clutch output disc 22 moves to the first clutch output disc 12 side, and as a result, the thrust washer is pressed against the first clutch output disc 12 side,
Thrust washer 33 and first clutch output disk 12
There is a possibility that a sufficient oil film will not be formed between the two.

Therefore, the thrust washer 33 in the third embodiment shown in FIG. 8 has the same overall shape as the thrust washer 32 in the second embodiment, and is provided with the same recess 73 and through groove 53. Further, a non-penetrating groove 6 is formed in the outer peripheral portion of the first clutch output disc 12 side.
3 is provided, and the groove 63 is formed from the rotation center axis (not shown).
The distance R1 to the most distal end portion 63a is larger than the distance R2 from the center axis of rotation to the inner peripheral surface of the second clutch output disk 22.

By doing so, the first clutch output disk 1 is moved as shown by arrows A2 to A5.
The lubricating oil that has flowed between the thrust washer 2 and the thrust washer 33 is collected in the non-penetrating groove 62, and the centrifugal hydraulic pressure of the lubricating oil is increased by increasing the radius of rotation, so that the lubricating oil flows in the axial direction of the second clutch output disc 22. It is possible to cancel the force that is applied to the first clutch output disc 12 side by the thrust washer due to the centrifugal hydraulic pressure that acts on the inner peripheral surface 22b of the extending portion. The lubricating oil flowing from the arrow A1 between the second clutch output disc 22 and the thrust washer 33 flows like A3 through the through groove 53 provided as in the above-described respective embodiments.

FIG. 9 is a view of the thrust washer 33 of the third embodiment as seen from the first clutch output disk 12 side, and the hatched portion is the area where the oil sump is formed.

FIG. 10 is an enlarged sectional view of the thrust washer portion of the fourth embodiment. In the thrust washer 34 according to the fourth embodiment, in order to obtain the same effect as that of the third embodiment, a recess 74 in which the recess 72 in the second embodiment is enlarged to the outer peripheral side is formed. There is. The surface of the thrust washer 34 on the side of the second clutch output disk 22 is provided with a through groove 54 similar to that in each of the above-mentioned embodiments, and the flow of lubricating oil indicated by each arrow is This is the same as the case of the third embodiment.

FIG. 11 is a view of the thrust washer 34 of the fourth embodiment as viewed from the first clutch output disk 12 side, and the mesh hatched portion is the area where an oil sump is formed. It is clear that the area where the oil sump is formed is large as compared with FIG. 9. Therefore, the same effect as that of the third embodiment can be obtained with a smaller number of processing steps.

FIG. 12 is an enlarged sectional view of the thrust washer portion of the fifth embodiment. In the thrust washer 35 according to the fifth embodiment, the same overall shape as that of the fourth embodiment is formed by only the iron plate, and
The surface on the side of the second clutch output disc 22 is tightly joined to the second clutch output disc 22 by welding. Therefore, the lubricating oil flowing into the hole 22a is indicated by the arrow A.
As in No. 6, all flows between the thrust washer 35 and the first clutch output disk 12, and does not flow at all between the second clutch output disk 22 and the thrust washer 35. With this configuration, the same effect as that of the fourth embodiment can be realized easily and at low cost.

FIG. 13 shows a thrust washer 30 of the prior art.
FIG. 14 is an enlarged sectional view showing a portion of FIG. 14, FIG. 14 is a view showing a single thrust washer 30, and FIG. 14A is a view seen from the first clutch output disc 12 side.
(B) is the figure seen from the 2nd clutch output disk 22 side. As in the first to fourth embodiments of the present invention, the first washer output disc 12 side of the thrust washer 30 is made of the slippery copper-based first member 30A and the second clutch output disc 12 is provided. The side of 22 is made of a high strength iron-based second member 30B.

In the prior art, a hole 22a formed in the second clutch output disk 22 as shown in the drawing.
Is larger than in each of the embodiments of the present invention, and contrary to the first to fourth embodiments of the present invention, the gap between the outer peripheral side (upper side in the drawing) of the claw 40 and the hole 22a. L1 may be larger than the gap L2 between the inner peripheral side (lower side in the figure) and the hole 22a.

Therefore, the amount of lubricating oil introduced into the oil chamber 122 as indicated by arrow A flows between the second clutch output disk 22 and the thrust washer as indicated by arrow A1.
The amount is larger than the amount flowing between the first clutch output disk 12 and the thrust washer 31 as indicated by arrow A2. Therefore, the thrust washer 30 is pushed toward the first clutch output disc 12 side.

Therefore, dimples (spherical depressions) 80 are formed on the surface of the thrust washer 30 on the side of the first clutch output disk 12 to store the lubricating oil, but at the same time a through groove 50 is formed. Therefore, the lubricating oil does not collect and escapes to the outer peripheral side, and eventually the lubricating oil easily runs out and sufficient lubrication cannot be performed. FIG. 15 is a sectional view taken along line XV-XV in FIG.
The cross-sectional shapes of the dimple (spherical recess) 80 and the through groove 50 are shown.

[0048]

According to the present invention, in a twin clutch type transmission, lubrication is provided between the member of the first clutch and the member of the second clutch that faces the member of the first clutch in the axial direction and relatively rotates. Sufficient oil is accumulated, lubrication is improved, friction is reduced, and abrasion and seizure are prevented.

[Brief description of the drawings]

FIG. 1 is an overall skeleton diagram of a twin clutch type transmission to which the present invention is applied.

2 is a first clutch C1, a second clutch C2, a first sleeve S1, a second sleeve S2, and a third sleeve S3 for obtaining each speed in the twin clutch type transmission of FIG.
It shows a combination of engagement of.

FIG. 3 is a cross-sectional view of a clutch portion according to the first embodiment.

FIG. 4 is an enlarged sectional view of a thrust washer portion according to the first embodiment.

5A and 5B are a single-part view of the thrust washer of the first embodiment, in which FIG. 5A is a view as seen from the transmission mechanism side, and FIG.
FIG. 6 is a view as seen along the line V-V in FIG.
(C) is the figure seen from the side opposite to the speed change mechanism part.

FIG. 6 is an enlarged cross-sectional view of a thrust washer portion of the second embodiment.

7A and 7B are single-part views of the thrust washer according to the second embodiment, in which FIG. 7A is a view seen from the side of a speed change mechanism unit, and FIG.
FIG. 7 is a view taken along line VII-VII of FIG.

FIG. 8 is an enlarged sectional view of a thrust washer portion according to a third embodiment.

FIG. 9 is a diagram of the thrust washer alone according to the third embodiment as viewed from the transmission mechanism side.

FIG. 10 is an enlarged sectional view of a thrust washer portion of a fourth embodiment.

FIG. 11 is a diagram of the thrust washer alone according to the fourth embodiment as viewed from the transmission mechanism side.

FIG. 12 is an enlarged sectional view of a thrust washer portion of a fifth embodiment.

FIG. 13 is an enlarged cross-sectional view of a thrust washer portion in a conventional technique.

FIG. 14 is a view showing a thrust washer according to the related art as a single item, in which (a) is a view as seen from the side of the transmission mechanism section, and (b) is a view showing the same.
FIG. 6 is a view seen from the side opposite to the transmission mechanism unit.

FIG. 15 is a view taken along line XV-XV in FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Clutch housing 2 ... Mission housing 3 ... Input shaft support part 3a ... 1st oil groove 3b ... 2nd oil groove 3c ... 3rd oil groove 4 ... Seal ring 5a, 5b, 5c, 5d ... Lip seal 10 ... Input shaft 10a ... 1st oil hole 10b ... 2nd oil hole 10c ... 3rd oil hole C1 ... 1st clutch C2 ... 2nd clutch 11 ... 1st clutch input disk 12 ... 1st clutch output disk 13 ... 1st clutch output shaft 14 ... first clutch / clutch plate 15 ... first clutch piston 16 ... first clutch / clutch disc 17 ... first clutch spring 115 ... first clutch piston oil chamber 21 ... second clutch input disc 22 ... second clutch output disc 22a ... Hole 23 ... Second clutch output shaft 24 ... Second clutch / clutch plate 25 ... Second clutch fix 26 ... 2nd clutch and clutch disc 27 ... 2nd clutch spring 28 ... Intermediate hub 29 ... 2nd clutch spring support disc 125 ... 2nd clutch piston oil chamber 30 ... Thrust washer (prior art) 31 ... Thrust washer (1st Embodiment 32 ... Thrust washer (second embodiment) 33 ... Thrust washer (third embodiment) 34 ... Thrust washer (fourth embodiment) 35 ... Thrust washer (fifth embodiment) Form: 41 ... Claws 50, 51, 52, 53, 54 ... Through groove 61, 63 ... Non-through groove 72, 73 ... Recessed portion 80 ... Dimple

Claims (2)

[Claims] 1. A first clutch for connecting and disconnecting an input shaft and a first speed change mechanism having a first speed ratio, and an input shaft and a second speed ratio arranged coaxially adjacent to the first clutch. A twin clutch transmission that has a second clutch that connects and disconnects a second speed change mechanism that has, and that achieves a plurality of shift speeds by controlling the connection and disconnection of the first clutch and the second clutch. A friction reducing member is interposed between a member and a member of the second clutch that faces the member of the first clutch and rotates relative to the member of the first clutch, and the friction reducing member is provided between the member of the first clutch and the second clutch. Of the friction reducing member, which is non-rotatably coupled to one of the members, and which extends from the inner diameter side end portion to the outer diameter side end portion and does not penetrate the surface on the side opposite to the coupled side. And the oil passage leading to the recess is formed. Forms with twin clutch transmission, characterized in that as the lubricating oil is accumulated in the recess guides the lubricating oil to the recess. 2. The centrifugal oil pressure of lubricating oil is provided by extending the outer diameter of the recess in the axial direction of either one of the first clutch member and the second clutch member to which the friction reducing member is coupled. The twin clutch type transmission according to claim 1, wherein the twin clutch type transmission has a larger inner diameter than that of the acting portion.