JP6747362B2 - Transmission friction plate, method of manufacturing transmission friction plate, and transmission - Google Patents

Description

The present invention relates to a transmission (for example, an automatic transmission) mounted on a vehicle, and more particularly to a transmission friction plate and a transmission friction plate used in a friction engagement device (for example, a clutch device and a braking device) of the transmission. The present invention relates to a manufacturing method and a transmission.

A friction plate described in Patent Document 1 is known as a friction plate used in a friction fastening device of an automatic transmission. This friction plate has a lubricating oil flow passage through which lubricating oil flows, and a plurality of discharge holes for discharging the lubricating oil from the lubricating oil flow passage to the friction surface on both sides of the friction surface. A plurality of lubricating oil passages are provided radially when the friction plate is viewed from the front, and the width of each lubricating oil passage is formed to be a constant width along the radial direction of the friction plate.

In this friction plate, the lubricating oil that has flowed into the lubricating oil flow path flows in the lubricating oil flow path from the inner peripheral edge side to the outer peripheral edge side of the friction plate due to the centrifugal force when the friction plate rotates, and at the same time, It is discharged from the lubricating oil flow path to the friction surface through the discharge hole of the surface. As described above, the friction plate is cooled by the lubricating oil flowing in the lubricating oil flow path of the friction plate, and the lubricating oil is discharged from the discharge holes to the friction surface of the friction plate (that is, the friction surface of the friction plate). Lubricating oil is supplied between the friction plates.

JP, 2012-215225, A

However, in the above-mentioned friction plate, the horizontal width of the lubricating oil passage is a constant width along the radial direction of the friction plate, so that the discharging pressure of the lubricating oil in each discharge hole is such that the discharge hole is at the outer peripheral side of the friction surface. The smaller it is, the smaller.

By the way, the discharge holes are provided, for example, in a load range of the friction surface of the friction plate (that is, a range in which the fastening load is relatively high). However, when the load range is distributed to the outer peripheral side of the friction surface, as described above. Since the discharge pressure of the lubricating oil in each discharge hole becomes smaller as the discharge hole is closer to the outer peripheral edge portion of the friction surface, the discharge pressure of the adjacent friction plate pressed to the load range of the friction surface of the friction plate is It cannot be pushed back by the lubricating oil discharged from the device, and the lubricating oil cannot be sufficiently supplied to the load range. In this case, it is necessary to increase the amount of lubricating oil supplied and push back the adjacent friction plate, but then, excessive lubricating oil is supplied to the load range, and the sliding resistance of the lubricating oil on the friction surface between each friction plate increases. To do.

Therefore, the present invention provides a friction plate for a transmission and a friction plate for a transmission that can supply lubricating oil with a sufficiently high hydraulic pressure in the load range even when the load range is distributed to the outer peripheral side of the friction surface of the friction plate. An object of the present invention is to provide a method for manufacturing the same and a friction plate for a transmission.

The present invention is a friction plate for a transmission, which is formed in a substantially annular shape with a plurality of teeth protruding outward in the radial direction at intervals on the outer peripheral side in the circumferential direction, and which are spaced apart from each other in the circumferential direction. And a pair of annular surface plates which are provided on both sides in the thickness direction of the plurality of core materials and sandwich the plurality of core materials from both sides, and a gap between the adjacent core materials. A lubricating oil flow path and a plurality of discharge holes provided in the annular surface plate for discharging lubricating oil from the inside of the lubricating oil flow path to the friction surface of the annular surface plate. A plurality of projecting portions that are provided at intervals in the circumferential direction and project outward in the radial direction are provided on the peripheral edge, and a portion on one side in the circumferential direction at the radially outer end of the core material is provided in the radial direction. The tip and the inner side surface of the protruding portion formed in a protruding shape match the contours of the tip and the side surface on one side of the tooth in a front view, and the core material is between the adjacent core material. In a state where the front and back are alternately replaced, the teeth are formed by radially outer ends of the plurality of core members arranged radially in a radial pattern and the protrusions, and the lubricating oil. The width of the flow passage in the circumferential direction is a friction plate for a transmission that gradually decreases from the inner peripheral edge side to the outer peripheral edge side of the annular surface plate.

According to this configuration, since the lateral width of the lubricating oil flow channel gradually decreases from the inner peripheral edge side of the annular surface plate toward the outer peripheral edge side, the lubricating oil flows inside the lubricating oil flow channel on the inner peripheral edge side of the annular surface plate. The hydraulic pressure of the lubricating oil can be increased as the oil flows from the outer peripheral edge side. Accordingly, even if the discharge hole is provided in the outer peripheral edge side portion of the friction surface, the discharge pressure of the lubricating oil in the discharge hole can be secured at a sufficiently high hydraulic pressure.

Therefore, even when the load range (that is, the range in which the fastening load is relatively high) is distributed to the outer peripheral side of the friction surface of the annular surface plate, the other friction plates pressed against the load range of the friction surface are relatively few. The lubricating oil can be pushed back by the amount of the lubricating oil and discharged from the discharging holes within the load range. As a result, in the transmission using this friction plate for the transmission, the minimum necessary lubricating oil can be discharged to the friction surface between the friction plates, and the sliding resistance of the lubricating oil on the friction surface between the friction plates can be reduced. You can

Further, as an aspect of the present invention, a partition part that partitions the lubricating oil flow path in the thickness direction of the core material may be provided.

According to this configuration, the lubricating oil flow passage can be divided into two lubricating oil flow passages, one on the side of the annular surface plate and the other side of the annular surface plate. Therefore, of the annular surface plates on both sides, the discharge pressure of the lubricating oil in the discharge hole of one annular surface plate and the discharge pressure of the lubricating oil in the discharge hole of the other annular surface plate are equal (that is, without deviation). Can be secured.

Further, the present invention is a manufacturing method for manufacturing the above-mentioned friction plate for a transmission, the core material having the plurality of core materials and a connecting portion connected to a tip end portion or a base end portion of each of the plurality of core materials. A step of forming a connecting body, a step of providing the pair of annular surface plates on both sides of the core material connecting body, and a step of providing the pair of annular surface plates on both sides of the core material connecting body; The method of manufacturing a friction plate for a transmission including the step of separating the friction plate from the core material.

With this configuration, when the pair of annular surface plates are provided on both sides of the plurality of core members, it is possible to prevent the plurality of core members from coming apart, and it is possible to improve the productivity of the transmission friction plate.

Further, the present invention is a transmission using the above-mentioned friction plate for a transmission, wherein at least one of the outer fastened member and the inner fastened member is rotatable about a predetermined rotation axis, and the outer fastened member. A first friction plate engaged with a member and a second friction plate engaged with the inner member to be fastened are alternately arranged, and the rotary shaft of the first friction plate and the second friction plate A friction plate set using the friction plate for a transmission as a friction plate rotatable around the holding plate, a holding member arranged on one side in the axial direction of the friction plate set, and on the other side in the axial direction of the friction plate set. And a piston arranged to press the friction plate set toward the holding member.

With this configuration, it is possible to provide a transmission having the effect of the above-mentioned transmission friction plate.

According to the present invention, even when the load range is distributed to the outer peripheral side of the friction surface of the friction plate, the friction plate for a transmission and the friction plate for a transmission can supply the lubricating oil with a sufficiently high hydraulic pressure in the load range. An object of the present invention is to provide a method for manufacturing the same and a friction plate for a transmission.

FIG. 3 is a cross-sectional view showing the upper half of the clutch device used in the transmission according to the first embodiment. The front view which shows a driven plate. (A) is a perspective view which shows a part of driven plate, (b) is an AA sectional view of (a). Sectional drawing which shows the internal structure of a driven plate. The disassembled perspective view which shows a part of disassembled state of a driven plate. The front view which shows a heartwood. Sectional drawing explaining the flow way of the lubricating oil in a clutch device. The front view which shows a part of core material connection body. The front view which shows some modifications of a core material connection body. (A) is a perspective view which shows a part of driven plate of 2nd Embodiment, BB sectional drawing of (b). Sectional drawing which shows the internal structure of a driven plate. The disassembled perspective view which shows a part of disassembled state of a driven plate. The front view which shows a core material and a partition part.

An embodiment of the present invention will be described below with reference to the drawings.
<First Embodiment>
<<Overall structure>>
A transmission 1 using a friction plate for a transmission according to an embodiment of the present invention will be described with reference to FIGS. 1 to 8. The friction plate for a transmission of the present invention is provided with the lubricating oil flow passage inside and the discharge hole for the lubricating oil is provided on the friction surface, thereby ensuring the minimum necessary lubricating oil while ensuring the cooling capacity of the friction plate. The friction resistance of the lubricating oil supplied between the friction plates is reduced.

The transmission 1 is, for example, an automatic transmission for an automobile, and by changing the gear ratio (=input shaft rotation speed/output shaft rotation speed of the transmission 1) according to the vehicle speed and the rotation speed of the engine, The output rotation is decelerated and output to the drive shaft.

Although not shown, the transmission 1 transmits the output rotation of the torque converter to which the output rotation of the engine is input, the plurality of planetary gear mechanisms, and among the plurality of planetary gear mechanisms described above. It is provided with a plurality of clutch devices (see FIG. 1) and a plurality of braking devices for switching the combination of planetary gear mechanisms. The gear ratio is switched by switching the combination of the planetary gear mechanisms to which the output rotation of the torque converter is transmitted by the clutch device and the brake device.

Each of the plurality of clutch devices described above is configured like the clutch device 3 shown in FIG. The clutch device 3 includes an input shaft 4 to which output rotation from a front stage (for example, the torque converter) is input, an output shaft 5 that outputs output rotation to a rear stage (for example, the sun gear of the planetary gear mechanism), and an input shaft. 4, a clutch drum 6 (an outer fastened member), a clutch hub 7 (an inner fastened member) fixed to the output shaft 5, and a friction plate disposed between the clutch drum 6 and the clutch hub 7. The set 8 includes, for example, an annular plate-shaped holding member 9 and a piston 10 for sandwiching the friction plate set 8 from both sides, and an annular retaining ring 11 for retaining the retaining member 9 to the clutch drum 6. .. Reference numeral K in FIG. 1 is the central axis of the input shaft 4 and the output shaft 5.

The input shaft 4 is rotatably supported and is fixed to an output shaft (not shown) in the preceding stage. The output shaft 5 is, for example, formed in a tubular shape, is concentrically arranged on the outer peripheral side of the input shaft 4 and is relatively rotatable, and is fixed to the clutch hub 7.

The clutch drum 6 includes an outer peripheral tubular portion 61, an inner peripheral tubular portion 65, and a bottom wall portion 66 that connects them, and is formed into, for example, an annular body having a substantially U-shaped cross section. The clutch drum 6 is concentrically fixed to the outer circumference of the input shaft 4. A plurality of splines 61a and a lubricating oil discharge hole 61b are provided on the inner peripheral surface of the outer peripheral tubular portion 61 of the clutch drum 6. Each spline 61a is a portion to which a tooth 81a of the driven plate 81, which will be described later, engages, and is provided along the axial direction of the clutch drum 6. The lubricating oil discharge hole 61b is a hole for discharging the lubricating oil supplied to the friction plate set 8 to the outside of the clutch drum 6, and is provided so as to penetrate in the thickness direction of the outer peripheral tubular portion 61.

The clutch hub 7 includes an outer peripheral cylinder portion 71 and a bottom wall portion 72 connected to the outer peripheral cylinder portion 71, and is formed by, for example, an annular body having a substantially inverted L-shaped cross section. The clutch hub 7 is concentrically arranged on the outer periphery of the input shaft 4 so as to be relatively rotatable, and is fixed to the output shaft 5. The outer peripheral tubular portion 71 of the clutch hub 7 is concentrically arranged inside the outer peripheral tubular portion 61 of the clutch drum 6 with a space therebetween. The outer peripheral cylinder portion 71 of the clutch hub 7 is provided with a plurality of splines 71a and a plurality of lubricating oil supply holes 71b. Each spline 71a is a portion with which a tooth 82a of the drive plate 82 described later is engaged, and is provided along the axial direction of the clutch drum 6. The lubricating oil supply hole 71b is a hole for supplying lubricating oil to the friction plate set 8, and is provided so as to penetrate in the thickness direction of the outer peripheral cylinder portion 71.

The friction plate set 8 includes a plurality of driven plates 81 and a plurality of drive plates 82. The driven plates 81 and the drive plates 82 are arranged concentrically and alternately with each other.

The driven plate 81 is made of metal and is formed in, for example, an annular plate shape (FIG. 2). A plurality of teeth 81a that engage with a plurality of splines 61a on the inner peripheral surface of the clutch drum 6 are provided on the outer peripheral surface of the driven plate 81 (FIG. 2). The driven plate 81 can rotate integrally with the clutch drum 6 by engaging the teeth 81a with the splines 61a.

The drive plate 82 is made of metal, for example, in a ring plate shape. On the inner peripheral surface of the drive plate 82, a plurality of teeth 82a that engage with the plurality of splines 71a on the outer peripheral surface of the clutch hub 7 are provided. The drive plate 82 is rotatable integrally with the clutch hub 7 by engaging the teeth 82a with the splines 61a.

A plurality of friction members 83 are provided on both main surfaces of the drive plate 82 over the entire circumferential direction. Each friction member 83 is formed of paper into a sheet shape, and can be impregnated with the lubricating oil supplied between the driven plate 81 and the drive plate 82.

A holding member 9 and a retaining ring 11 are arranged in this order from the friction plate set 8 side on one side in the axial direction of the friction plate set 8, and, for example, an annular buffer plate 21 is arranged on the other side in the axial direction of the friction plate set 8. A piston 10 is arranged therethrough.

The retaining ring 11 is mounted in a groove 61c provided on the inner peripheral surface of the outer peripheral tubular portion 61 of the clutch drum 6, and is fixed to the clutch drum 6 by this mounting. The holding member 9 is retained by the clutch drum 6 by being caught by the retaining ring 11.

The piston 10 includes an outer peripheral cylindrical portion 13 and a bottom wall portion 14 connected to the outer peripheral cylindrical portion 13, and is formed into, for example, an L-shaped annular body having a substantially vertical cross section. The piston 10 is arranged inside the clutch drum 6 so as to be movable in the axial direction of the friction plate set 8. The piston 10 includes a pressing portion 12 that presses the friction plate set 8, and the pressing portion 12 presses the friction plate set 8 toward the holding member 9 side via the buffer plate 21. The pressing portion 12 is formed in a flange shape protruding from the tip of the outer peripheral cylindrical portion 13 of the piston 10 toward the outer peripheral side.

The clutch drum 6 further includes a hydraulic chamber 62 and a spring accommodating chamber 64. The hydraulic chamber 62 is a portion for storing hydraulic oil that presses the piston 10 toward the friction plate set 8 side, and is adjacently provided on the opposite side of the piston 10 from the friction plate set 8 side. The spring accommodating chamber 64 is a portion for accommodating the winding spring 63 that biases the piston 10 to the side opposite to the friction plate set 8, and is adjacent to the friction plate set 8 side of the piston 10. The hydraulic chamber 62 and the spring accommodating chamber 64 are partitioned by the piston 10. The piston 10 moves to the friction plate set 8 side or the opposite side according to the magnitude relation between the hydraulic pressure of the hydraulic oil in the hydraulic chamber 62 and the biasing force of the winding spring 63 in the spring accommodating chamber 64. There is.

In the clutch device 3, when the hydraulic oil is supplied to the hydraulic chamber 62, the hydraulic oil in the hydraulic chamber 62 moves the piston 10 to the spring accommodating chamber 64 side. By this movement, the pressing portion 12 of the piston 10 presses the friction plate set 8 toward the holding member 9 side, and by this pressing, the driven plates 81 and the drive plates 82 in the friction plate set 8 are pressed toward the holding member 9 side. The adjacent plates 81 and 82 are fastened to each other by the frictional resistance generated between the plates 81 and 82. By this fastening, the clutch drum 6 and the clutch hub 7 are fastened via the friction plate set 8. By this fastening, the rotational power input to the input shaft 4 is transmitted to the output shaft 5 and output from the output shaft 5. Then, when the supply of hydraulic oil to the hydraulic chamber 62 is released, the hydraulic pressure of the hydraulic oil in the hydraulic chamber 62 decreases, and the urging force of the winding spring 63 moves the piston 10 in the direction away from the holding member 9. By this movement, the frictional resistance between the plates 81 and 82 is reduced, and the engagement between the clutch drum 6 and the clutch hub 7 is released.

In the above description, when the pressing portion 12 presses the friction plate set 8, the pressing force (that is, the fastening load) is transmitted from the pressing surface 12a of the pressing portion 12 to the mounting portion 11a of the retaining ring 11 with the clutch drum 6. To do. That is, the pressing force is mainly transmitted along the linear strip area C1 that connects the pressing surface 12a of the pressing portion 12 and the mounting portion 11a of the retaining ring 11. Therefore, a relatively high fastening load acts on a range (hereinafter, referred to as a load range) C2 (FIG. 2) that intersects with the linear strip region C1 of each of the plates 81 and 82.

As shown in FIG. 2, for example, in the driven plate 81, the load range C2 is formed in an annular shape so as to occupy a fixed section in the radial direction of the driven plate 81 and to cover the entire circumferential direction. The radial position and the radial width of the load range C2 in the driven plate 81 differ depending on the position of the driven plate 81 in the friction plate set 8 (for example, the position from the pressing portion 12 side). ing. In FIG. 2, the load range C2 is formed, for example, near the center in the radial direction. Note that the drive plate 82 also has a load range C2 as in the driven plate 81.

<<Structure of driven plate 81>>
In this embodiment, the transmission friction plate of the present invention is applied to, for example, the driven plate 81. As shown in FIGS. 2 to 4, the driven plate 81 is provided in the lubricating oil passage 81b provided inside and the friction surfaces 81c on both sides, and the lubricating oil flowing in the lubricating oil passage 81b is applied to the friction surface 81c. The discharge hole 81d for discharging is provided. An inlet 81e of the lubricating oil passage 81b is provided on the inner peripheral surface of the driven plate 81, and an outlet 81f of the lubricating oil passage 81b is provided on the outer peripheral surface of the driven plate 81 (FIG. 4). ..

More specifically, as shown in FIG. 5, the driven plate 81 is provided with a plurality of core members 85 annularly arranged at intervals and a plurality of core members 85 provided on both sides in the thickness direction of the core members 85. And a pair of annular surface plates 86 sandwiching 85 from both sides in the thickness direction.

As shown in FIG. 6, the core material 85 is made of metal and is formed in a flat plate shape having a small piece in a front view. In the core material 85, for example, a belt-shaped load range C2 is formed in the vicinity of the center in the vertical direction (that is, the radial direction H1) over the entire lateral direction (that is, the circumferential direction H2). The lateral width (that is, the width in the circumferential direction H2) W1 of the core material 85 becomes maximum in the load range C2 of the core material 85, and goes from the load range C2 toward the base end portion (that is, the end portion inside the radial direction H1) 85d (that is, the annular shape). It gradually becomes smaller (toward the inner peripheral edge 86a side of the surface plate 86). That is, the side surfaces 85e, 85f on both sides of the core material 85 in the circumferential direction H2 are inclined toward the inner side in the circumferential direction H2 toward the proximal end portion 85d in the portion 85c closer to the proximal end portion 85d than the load range C2. The radial direction H1 and the circumferential direction H2 are the radial direction and the circumferential direction of the annular surface plate 86 (and thus the driven plate 81), respectively.

A portion 85a1 on one side in the circumferential direction H2 of the tip portion (that is, the end portion on the outer side in the radial direction H1) 85a of the core material 85 is formed in a substantially arc shape, and extends substantially along the arc of the outer peripheral surface of the driven plate 81. On the other hand, on the other hand, the portion 85a2 on the other side in the circumferential direction H2 is formed in a projecting shape projecting in the radial direction H1, and the front end and the contour of the inner side surface have one end of the tooth 81a of the driven plate in a front view. And conform to the side profile. Hereinafter, the circular arc portion 85a1 and the protruding portion 85a2 will also be referred to. The lateral width W1 of the intermediate portion 85b of the core material 85 between the load range C2 and the tip 85a is formed to be substantially the same as the lateral width W1 in the load range C2.

The plurality of core members 85 are arranged radially around the center of the driven plate 81, and are also arranged in an annular shape with a space therebetween. The plurality of core materials 85 are arranged such that the front and back sides of the adjacent core materials 85 are alternately interchanged. The side surfaces 85f of the adjacent core members 85 on the protruding portion 85a2 side face each other with a space therebetween, and the side faces 85e of the adjacent core members 85 on the arc portion 85a1 side face each other with a space therebetween. The space between the adjacent core materials 85 extends in the radial direction H1 and is open at both ends in the radial direction H1.

As shown in FIG. 6, each lubricating oil flow path 81b is formed by a space (gap) between the adjacent core materials 85. The inflow port 81e and the outflow port 81f of each lubricating oil flow path 81b are formed by the inner open end and the outer open end of the space between the adjacent cores 85 in the radial direction H1. The lateral width (that is, the width in the circumferential direction H2) W2 of the lubricating oil flow path 81b is from the base end portion 85d side of the core member 85 toward the tip end portion 85a side (that is, from the inner peripheral edge side to the outer peripheral edge side of the annular surface plate 86). ) It is getting smaller and smaller. More specifically, the lateral width W2 of each lubricating oil flow path 81b gradually decreases from the base end portion 85d to the load range C2, becomes the minimum in the load range C2, and becomes substantially the same from the load range C2 to the tip end portion 85a. It has a certain width.

As shown in FIG. 5, each annular surface plate 86 is made of a metal and formed into an annular plate shape. A plurality of protrusions 86c are provided on the outer peripheral edge of each annular surface plate 86. The protrusions 86c are provided at intervals in the circumferential direction H2 and project outward in the radial direction H1, and constitute the teeth 81a of the driven plate 81 together with the protrusions 85a2 of the core material 85.

Each of the annular surface plates 86 is provided with the above-described plurality of ejection holes 81d. Each discharge hole 81d is provided in a region overlapping with each lubricating oil flow path 81b, and penetrates in the thickness direction of each annular surface plate 86. The density of each discharge hole 81d is relatively higher in the load range C2 of the friction surface of each annular surface plate 86 (that is, the friction surface 81c of the driven plate 81), and is closer to the inner peripheral edge side and the outer peripheral edge side than the load range C2. Is relatively low. In this embodiment, the density of the discharge holes 81d is, for example, zero in a portion of the friction surface of the annular surface plate 86 on the outer peripheral side of the load range C2.

In a state in which the plurality of core materials 85 are sandwiched between the respective annular surface plates 86, the respective annular surface plates 86 and the plurality of core materials 85 are, for example, diffusion-bonded (that is, the annular surface plate 86 and the core material 85 are heated and pressed, The joining method of joining using diffusion of) is joined. In this joined state, as shown in FIG. 6, in a front view, the base end portion 85d of each core material 85 is adjacent to the inner peripheral edge 86a of the annular surface plate 86, and the protruding portion 85a2 of each core material 85 is formed in each annular surface. It is fitted to one side of the protruding portion 86c of the face plate 86. That is, the length of each annular surface plate 86 in the radial direction H1 and the length of each core material 85 in the radial direction H1 are formed to be substantially the same.

<<Flow of lubricating oil>>
As shown in FIG. 7, the lubricating oil Q is supplied to the space between the clutch hub 7 and the clutch drum 6 from each lubricating oil supply hole 71 b of the outer peripheral cylinder portion 71 of the clutch hub 7. The supplied lubricating oil Q flows into each lubricating oil passage 81b from each inlet 81e on the inner peripheral surface of the driven plate 81. Then, the inflowing lubricating oil Q flows in each lubricating oil flow passage 81b from the inflow port 81e side to the outflow port 81f side (that is, from the inner side to the outer side in the radial direction H1) by the centrifugal force generated by the rotation of the driven plate 81. .. Then, a part of the lubricating oil Q is discharged from each discharge hole 81d of the friction surface 81c of the driven plate 81 to the friction surface 81c (that is, between the driven plate 81 and the drive plate 82), and the rest of the lubricating oil Q is lubricated. The oil flows out of the lubricating oil flow path 81b from the outlet 81f of the oil flow path.

As the lubricating oil Q flows in the lubricating oil passage 81b as described above, the friction heat generated in the driven plate 81 is cooled. Further, the lubricating oil Q discharged from the discharge hole 81d of the driven plate 81 to the friction surface 81c reduces the friction on the friction surface between the driven plate 81 and the drive plate 82.

At the time of the above-described discharge, the density of each discharge hole 81d is relatively high in the load range C2 of the friction surface 81c of the driven plate 81, so that the density is relatively large in the load range C2 of the friction surface 81c of the driven plate 81. Lubricating oil Q is supplied.

Further, during the above-described discharge, the lateral width W2 of each lubricating oil flow passage 81b extends from the inlet 81e side of the lubricating oil flow passage 81b toward the outlet 81f side (that is, from the inner peripheral edge side to the outer peripheral edge side of the annular surface plate 86). The oil pressure of the lubricating oil Q increases from the inlet 81e side of the lubricating oil flow passage 81b toward the outlet 81f side of the lubricating oil flow passage 81b, and reaches the maximum in the load range C2. Therefore, the lubricating oil Q is discharged with sufficiently high hydraulic pressure from the respective discharge holes 81d within the load range C2 of the friction surface 81c of the driven plate 81. As a result, the adjacent drive plate 82 pressed against the load range C2 of the friction surface 81c of the driven plate 81 can be pushed back with a relatively small amount of lubricating oil Q.

That is, in order to discharge the lubricating oil Q from the discharge hole 81d within the load range C2, it is necessary to push back the adjacent drive plate 82 that is pressed against the load range C2 of the friction surface 81c. Since the lubricating oil Q is discharged from each discharge hole 81d in the range C2 with a sufficiently high hydraulic pressure, it is only necessary to discharge a relatively small amount of the lubricating oil Q from the discharge hole 81d in the load range C2 to the load range C2. The adjacent drive plate 82 that has been pressed can be pushed back. As a result, the minimum necessary lubricating oil Q can be discharged to the friction surface between the driven plate 81 and the drive plate 82, and the sliding resistance of the lubricating oil Q on the friction surface between the plates 81 and 82 can be reduced.

Further, the lubricating oil Q flowing out from the outlet 81f of the lubricating oil flow passage 81b flows between the clutch drum 6 and the driven plate 81, and the like, so that the lubricating oil Q is discharged from the lubricating oil discharge hole 61b on the outer peripheral surface of the clutch drum 6. 6 is discharged to the outside.

<< Manufacturing method of driven plate 81 >>
The driven plate 81 is manufactured as follows. That is, as shown in FIG. 8, first, the core material connecting body 90 is formed. The core material connecting body 90 includes a plurality of core materials 85 and a connecting portion 87 integrally formed with the plurality of core materials 85. As described above, the plurality of core members 85 are arranged in a ring shape with a space therebetween, and are also arranged radially. The connecting portion 87 is formed in an annular shape, is arranged on the outer peripheral side of the plurality of core materials 85, and is connected to the respective tip portions 85 a of the plurality of core materials 85.

Then, a pair of annular surface plates 86 are joined to both sides of the core material connecting body 90 by, for example, diffusion joining. Then, after the joining, the connecting portion 87 is separated from the plurality of core materials 85. In this way, the driven plate 81 is manufactured.

≪Main effect≫
As described above, according to the friction plate for a transmission according to this embodiment, a plurality of core members 85 arranged in an annular shape with a space between each other and provided on both sides of the plurality of core members 85, and sandwiching the plurality of core members 85 from both sides. A pair of annular surface plates 86, a lubricating oil flow channel 81b formed by a gap between adjacent core members 85, and the annular surface plate 86 are provided in the lubricating oil flow channel 81b. A plurality of discharge holes 81d for discharging to the friction surface 81c are provided, and the lateral width W2 of the lubricating oil flow path 81b gradually decreases from the inner peripheral edge side to the outer peripheral edge side of the annular surface plate 86 (see FIG. 6). ).

According to this configuration, since the lateral width W2 of the lubricating oil flow passage 81b gradually decreases from the inner peripheral edge side of the annular surface plate 86 toward the outer peripheral edge side thereof, the lubricating oil flows inside the lubricating oil flow passage 81b in the annular surface plate The hydraulic pressure of the lubricating oil can be increased as the fluid flows from the inner peripheral edge side of 86 to the outer peripheral edge side. As a result, even if the discharge hole 81d is provided in the outer peripheral edge side portion of the friction surface 81c, the discharge pressure of the lubricating oil in the discharge hole 81d can be secured at a sufficiently high hydraulic pressure.

Therefore, even when the load range C2 is distributed to the outer peripheral edge side portion of the friction surface of the annular surface plate 86, the drive plate 82 (another friction plate) pressed against the load range C2 of the friction surface of the annular surface plate 86 is relatively moved. The lubricating oil can be pushed back by a small amount of the lubricating oil and discharged from the discharge hole 81d within the load range C2. As a result, when this friction plate for a transmission is used in a transmission, the minimum necessary amount of lubricating oil can be discharged to the friction surface between the friction plates, and the sliding resistance of the lubricating oil on the friction surface between the friction plates is reduced. be able to.

Further, since the density of the plurality of discharge holes 81d is relatively high in the load range C2 of the friction surface of the annular surface plate 86 (see FIG. 4), it is sufficient for the load range C2 of the friction surface of the annular surface plate 86. A large amount of lubricating oil can be supplied.

Further, since the lateral width W1 of the core material 85 becomes maximum in the load range C2 of the core material 85 and gradually decreases from the load range C2 to the inner peripheral edge side of the annular surface plate 86 (see FIG. 6), the lubricating oil The lateral width W2 of the flow path 81b can be minimized in the load range C2 on the friction surface of the annular surface plate 86, and can be made smaller from the load range C2 toward the inner peripheral edge side of the annular surface plate 86. As a result, the lubricating oil can be discharged with a sufficiently high hydraulic pressure from each discharge hole 81d within the load range C2 of the friction surface 81c of the driven plate 81.

Moreover, since the lateral width W1 of the core material 85 is maximized in the load range C2, the volume of the core material 85 in the load range C2 can be increased. As a result, the heat capacity in the load range C2, which is the heat generating portion, can be increased, and the temperature rise in the load range C2 can be suppressed.

Further, according to the method for manufacturing a friction plate for a transmission according to this embodiment, a core material linked body 90 having a plurality of core materials 85 and a connecting portion 87 connected to the respective tip portions 85a of the plurality of core materials 85 is formed. And a step of providing a pair of annular surface plates 86 on both sides of the core material connecting body 90, and after providing a pair of annular surface plates 86 on both sides of the core material connecting body 90, the connecting portion 87 is separated from the plurality of core materials 85. Since the steps are included (see FIG. 8), it is possible to prevent the plurality of core members 85 from coming apart when providing the pair of annular surface plates 86 on both sides of the plurality of core members 85, and to improve the productivity of the friction plate for a transmission. Can be improved.

In this embodiment, the connecting portion 87 is connected to the distal end portions 85a of the plurality of core members 85, but as shown in FIG. 9, the connecting portion 87 is a base end portion of each of the plurality of core members 85. It may be connected to 85d. In this case, the connecting portion 87 is formed in a ring shape, is arranged inside the plurality of core materials 85 arranged in a ring shape, and is connected to the respective base end portions 85 d of the plurality of core materials 85. Also in this case, the same effect as in the case where the connecting portion 87 is connected to the respective tip portions 85a of the plurality of core members 85 can be obtained.

Further, according to the transmission 1 according to this embodiment, at least one of the clutch drum 6 (the outer member to be fastened) and the clutch hub 7 (the inner member to be fastened), which are rotatable about the rotation axis, is connected to the clutch drum 6. The driven plate 81 (first friction plate) engaged and the drive plate 82 (second friction plate) engaged with the clutch hub 7 are alternately arranged. Of the driven plate 81 and the drive plate 82, A friction plate set 8 using the above-mentioned transmission friction plate on a friction plate (a driven plate 81 in this embodiment) rotatable about a rotation axis, and a holding member arranged on one axial side of the friction plate set 8. Since the member 9 and the piston 10 that is arranged on the other axial side of the friction plate set 8 and presses the friction plate set 8 toward the holding member 9 side are provided (see FIG. 1 ), the above-mentioned friction plate for a transmission is provided. A transmission having an effect can be provided.

<Second Embodiment>
As shown in FIGS. 10 to 13, in the driven plate 81 of this embodiment, in the driven plate 81 of the first embodiment described above, each lubricating oil flow passage 81b is divided into two parts in the thickness direction of the core material 85. The part 88 is provided. In other words, the partition 88 divides the lubricating oil flow passage 81 b into two in the thickness direction of the core material 85.

The partition portion 88 is formed in a flat plate shape thinner than the thickness of the core material 85. The partition portion 88 is provided across the side surfaces 85f (or between the side surfaces 85e) of the adjacent core materials 85. More specifically, the sides of the partition portion 88 on both sides in the circumferential direction H2 are formed in a shape that matches the shape of the side surfaces 85f (or the side surface 85e) on both sides in the circumferential direction H2 of the core material 85 when viewed from the front of the core material 85. (Fig. 13). The partition portion 88 is connected to the middle of the side surface 85f (or the side surface 85e) of the core material 85 in the lateral width direction (that is, the thickness direction of the core material 85), and from one end to the other end in the longitudinal direction of the side surface 85f (or side surface 85e). Is continuously connected to the core material 85.

According to this configuration, the lubricating oil flow passage 81b can be divided into two lubricating oil flow passages, one annular surface plate 86 side and the other annular surface plate 86 side. As a result, of the annular surface plates 86 on both sides, the discharge pressure of the lubricating oil in the discharge hole 81d of the one annular surface plate 86 and the discharge pressure of the lubricating oil in the discharge hole 81d of the other annular surface plate 86 are set. It can be ensured evenly (that is, without bias).

In the correspondence between the configuration of the present invention and the above-described embodiment,
The clutch drum of the present invention corresponds to the outer fastened member of the embodiment,
Similarly below
The clutch hub corresponds to the inner fastened member,
The driven plate corresponds to the first friction plate,
The drive plate corresponds to the second friction plate,
The present invention is not limited to the configurations of the above-described embodiments.

In this embodiment, the transmission friction plate of the present invention is applied to the driven plate 81, but may be applied to the drive plate 82. Further, although the friction plate for a transmission of the present invention is applied to the friction plate of the clutch device of the transmission 1, it may be applied to the friction plate of the braking device of the transmission 1.

As described above, the present invention relates to a transmission (for example, an automatic transmission) mounted on a vehicle, and more particularly to a transmission friction plate used in a friction engagement device (for example, a clutch device and a brake device) of the transmission. It is useful.

1... Transmission 6... Clutch drum (externally fastened member)
7... Clutch hub (inner fastened member)
8... Friction plate set 9... Holding member 10... Piston 81... Driven plate (first friction plate)
81b... Lubricating oil flow path 81d... Discharge hole 82... Drive plate (second friction plate)
85... Heart material 86... Annular surface plate 87... Connection part 88... Partition part 90... Heart material connection body C2... Load range W1... Horizontal width of core material W2... Horizontal width of lubricating oil flow path

Claims (4)

A friction plate for a transmission, which is formed in a substantially annular shape in which a plurality of teeth protruding outward in the radial direction are formed at intervals on the outer peripheral side in the circumferential direction,
A plurality of core materials arranged in an annular shape at intervals in the circumferential direction,
A pair of annular surface plates provided on both sides in the thickness direction of the plurality of core members, and sandwiching the plurality of core members from both sides,
A lubricating oil flow path formed by a gap between adjacent core materials;
A plurality of discharge holes provided in the annular surface plate, for discharging lubricating oil from the inside of the lubricating oil channel to the friction surface of the annular surface plate,
The outer peripheral edge of the annular surface plate is provided with a plurality of projecting portions that are provided at intervals in the circumferential direction and project outward in the radial direction,
A portion on one side in the circumferential direction at the radially outer end portion of the core member is formed in a projecting shape that projects in the radial direction, and the tip and the inner side surface of the projecting portion are one side of the tooth in front view. Match the contours of the tip and side of
The core material is arranged radially in a state in which the front and back are alternately interchanged with the adjacent core material,
The teeth are formed by the radially outer ends and the protrusions of the plurality of core members that are annularly arranged at intervals from each other,
The friction plate for a transmission, wherein the circumferential width of the lubricating oil flow passage is gradually reduced from the inner peripheral edge side to the outer peripheral edge side of the annular surface plate. The friction plate for a transmission according to claim 1, further comprising a partition portion that partitions the lubricating oil flow path in a thickness direction of the core material. A manufacturing method for manufacturing the friction plate for a transmission according to claim 1 or 2,
A step of forming a core material connecting body having the plurality of core materials and a connecting portion connected to the front end portion or the base end portion of each of the plurality of core materials;
Providing the pair of annular surface plates on both sides of the core material connecting body,
A method of manufacturing a friction plate for a transmission, comprising the steps of providing the pair of annular surface plates on both sides of the core material connecting body and then separating the connecting portion from the plurality of core materials. A transmission using the transmission friction plate according to claim 1 or 2 ,
An outer fastened member and an inner fastened member, at least one of which is rotatable about a predetermined rotation axis;
First friction plates engaged with the outer member to be fastened and second friction plates engaged with the inner member to be fastened are alternately arranged, and the first friction plate and the second friction plate Of these, a friction plate set using the friction plate for the transmission in the friction plate rotatable about the rotation shaft,
A holding member arranged on one side in the axial direction in the friction plate set,
A transmission provided with a piston arranged on the other side in the axial direction of the friction plate set and pressing the friction plate set toward the holding member.

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