JP2007271016A - Automatic transmission and method for manufacturing rotary member used for the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To evenly supply sufficient lubricating oil to a friction engagement element without cost increase by improving drawing out from a die in die-casting of a rotary member. <P>SOLUTION: In an automatic transmission provided with a transmission device 13 including a plurality of friction engagement element comprising a clutch and a brake, and including a bottomed cylinder shape rotary member 45, the rotary member includes a hub member 70 extending in a direction opposite to opening direction of the rotary member from a bottom part 53 of the rotary member and engaging with a friction element of the friction engagement element by spline, and at least part of draft in a circumference direction of an inner circumference surface of a hub member is inclined in a direction in which a diameter expands as it goes toward the opening direction of the rotary member. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an automatic transmission including a transmission having a plurality of friction engagement elements including a clutch and a brake, and a method of manufacturing a rotating member used therefor.

As described in Patent Document 1, as an automatic transmission used in a vehicle such as an automobile, a bottomed cylindrical drum, a friction engagement element disposed in the drum, and a boss portion of the drum A clutch that is slidably disposed on the top and that forms a cylinder chamber together with the drum and has a piston that can press the frictional engagement element with the pressure oil supplied to the cylinder chamber, and a drum formed on the drum Some include frictional engagement elements disposed on the outer periphery of the hub portion. In the thing of this patent document 1, since the drum is formed by flow forming, there exists a problem which manufacturing cost rises.
Japanese Patent Laid-Open No. 10-296365

  As a drum forming method that can solve the above problems, it is conceivable to form a drum by a die-casting method. However, when the drum is formed by die-casting, it is necessary to provide a draft angle for mold release in the hub portion in which the friction engagement element is disposed on the outer periphery. For this reason, the hub portion is provided on the inner periphery of the hub portion. A gradient whose diameter increases toward the end of the part is formed.

  For this reason, when supplying oil for lubricating the friction engagement element from the inner peripheral side of the hub part through the oil hole penetrating in the radial direction of the hub part, the oil supplied to the inner periphery of the hub part is A large amount of oil flows along the draft on the end side of the hub portion, and the oil hole located on the side opposite to the end portion side of the hub portion causes a problem that the supply of lubricating oil becomes uneven.

  In order to avoid such a situation, after die casting, the draft formed on the inner periphery of the hub part is removed by cutting, or a weir made of a snap ring or the like is provided at the inner peripheral end of the hub part. It is conceivable to make the supply of lubricating oil uniform to the frictional engagement elements by securing an oil sump, etc., but either idea increases the manufacturing process and causes a cost increase.

  The present invention improves the die-cutting when a rotary member such as a clutch drum is die-cast, thereby automatically supplying sufficient lubricating oil to the friction engagement elements without increasing the cost. An object of the present invention is to provide a transmission and a method of manufacturing a rotary member used therefor.

  In order to solve the above-mentioned problem, the invention according to claim 1 is provided with a transmission having a plurality of friction engagement elements including a clutch and a brake, and the transmission is molded by die casting. In the automatic transmission having a cylindrical rotating member, the rotating member extends from the bottom of the rotating member in a direction opposite to the opening direction of the rotating member, and a hub member that splines engages the friction element of the friction engaging element on the outer periphery. The hub member is disposed so that at least a part thereof overlaps the bottom of the rotating member in the axial direction, and at least a part of the draft angle in the circumferential direction of the inner periphery of the hub member is It is characterized in that it is inclined in a direction in which the diameter increases as it goes in the opening direction of the member.

  According to a second aspect of the present invention, in the first aspect, the transmission includes oil supply means for supplying lubricating oil for lubricating the friction element on the radially inner peripheral side of the hub member. The member has at least one oil hole for supplying the lubricating oil supplied from the oil supply means to the friction element.

  According to a third aspect of the present invention, in the first or second aspect of the present invention, a plurality of die-cutting holes at the time of die-casting that penetrates in the axial direction are formed on the bottom of the rotating member on the circumference, An inclined surface that is inclined in a direction in which the diameter increases toward the opening direction of the rotating member is formed in a part of the inner circumferential direction of the hub member corresponding to the die-cutting hole. is there.

  According to a fourth aspect of the present invention, in the third aspect of the present invention, torque transmission is not performed on the inner peripheral side of the punching hole at the bottom of the rotating member.

  According to a fifth aspect of the present invention, in the fourth aspect, the rotating member is a clutch drum that forms a hydraulic servo of a clutch that is one of the plurality of friction engagement elements. A cylinder oil chamber of the hydraulic servo is formed on the radially inner peripheral side of the punching hole.

  According to a sixth aspect of the present invention, in any one of the third to fifth aspects, the rotating member has an outer peripheral wall and an inner peripheral wall extending in an axial direction from the bottom portion, and the bottom portion is the mold. A first wall portion is provided on the radially inner peripheral side of the punching hole, and the hub member extends across both axial sides of the first wall portion on the outer peripheral side of the first wall portion. It is characterized by.

  According to a seventh aspect of the present invention, in the sixth aspect of the present invention, in the outer peripheral wall of the rotating member, a discharge hole that discharges oil that has flowed into the rotating member through the punching hole to the outside of the rotating member. Is opened in the radial direction.

  The invention according to claim 8 provides the oil supply means according to any one of claims 2 to 7, wherein the oil supply means guides the lubricating oil supplied from an oil supply source toward an inner periphery of the hub member. It has the guide member provided with the guide part, It is characterized by the above-mentioned.

  The invention according to claim 9 is the invention according to claim 8, wherein the inner peripheral surface of the hub member is inclined in a direction in which the diameter increases from a predetermined position away from the die punching hole toward the opening direction of the rotating member. The first inclined surface, and a second inclined surface inclined in a direction in which the diameter increases from the predetermined position toward the direction opposite to the opening direction of the rotating member.

  A tenth aspect of the present invention is the first aspect of the first to eighth aspects, wherein the inner circumference of the hub member is inclined in a direction in which the diameter increases toward the opening direction of the rotating member. In addition to forming an inclined surface, a protruding dam is integrally formed on the inner periphery of the end portion of the hub member in the axial direction opposite to the opening direction of the rotating member.

  The invention according to claim 11 is provided with a transmission having a plurality of friction engagement elements consisting of a clutch and a brake, and the transmission has a bottomed cylindrical rotating member formed by die casting. The transmission includes an outer peripheral wall extending in the axial direction, an inner peripheral wall extending in the axial direction, a bottom wall connecting the outer peripheral wall and the inner peripheral wall, and a hub member extending from the bottom wall in a direction opposite to the outer peripheral wall. The first and second molds forming the cavity for forming the rotating member are used, and one of the first and second molds penetrates the cavity portion forming the bottom wall and the inner periphery of the hub member. And a first mold part for die cutting that molds a first inclined surface that is inclined in a direction in which the diameter increases as it goes in the opening direction of the rotating member.

  According to a twelfth aspect of the present invention, in the eleventh aspect, the other of the first and second molds is contacted with the first mold portion at a predetermined position away from the cavity portion forming the bottom wall. In this method, a second mold part is formed on the inner periphery of the hub member so as to simultaneously mold a second inclined surface having a reverse gradient to the first inclined surface.

  A thirteenth aspect of the present invention is the method according to the eleventh aspect, wherein a gap is provided between a tip end portion of the first mold portion of the first mold and the second mold, and the hub member is formed by the gap. This is a method characterized in that a weir is simultaneously formed on the inner periphery.

  According to the first aspect of the present invention, the bottomed cylindrical rotating member formed by die casting has a hub member extending from the bottom of the rotating member in a direction opposite to the opening direction of the rotating member, The member is arranged so that at least a part thereof overlaps with the bottom of the rotating member in the axial direction, and at least a part of the draft angle in the circumferential direction of the inner periphery of the hub member is increased in diameter toward the opening direction of the rotating member. In the case where oil is supplied to the inner periphery of the hub member, it is possible to prevent the oil from escaping from the end side of the hub member due to the draft angle. Thus, the oil can be securely held, and the amount of lubricating oil to the friction engagement element can be increased.

  According to the invention of claim 2, the transmission has oil supply means for supplying lubricating oil for lubricating the friction element on the radially inner peripheral side of the hub member, and the hub member is supplied from the oil supply means. Since at least one oil hole for supplying the lubricated oil to the friction element is provided, the oil supplied to the inner periphery of the hub member by the oil supply means passes along the inclined surface of the hub member from the oil hole at the bottom of the rotating member. It becomes possible to reliably supply the friction engagement element on the outer peripheral side, and the friction engagement element can be properly lubricated.

  According to the third aspect of the present invention, a plurality of die-cutting holes are formed on the bottom of the rotary member at the time of die-casting that penetrates in the axial direction on the circumference, and the inside of the hub member corresponding to the die-cutting hole Since an inclined surface that is inclined in a direction in which the diameter increases as it goes in the opening direction of the rotating member is formed in a part of the circumferential direction of the periphery, it can be easily opened in the inner periphery of the hub member by forming a hole for die cutting A directional slope can be formed.

  According to the invention of claim 4, by not transmitting torque on the inner peripheral side from the die-cutting hole at the bottom of the rotating member, high rigidity of the inner peripheral member is not required, and the effect of forming the die-cutting hole Can be reduced.

  According to the invention of claim 5, the rotating member is a clutch drum that forms a hydraulic servo of the clutch, and a cylinder oil chamber of the hydraulic servo is formed on the clutch drum on the radially inner side of the punching hole. Therefore, the bottom portion of the clutch drum in which the hole for punching is formed only needs to have a function of disposing a hydraulic servo, and is a portion not directly involved in torque transmission. Therefore, even if the punching hole is formed at the bottom of the clutch drum, there is no problem in strength. Further, by forming the cylinder oil chamber at a position overlapping with the hub member in the axial direction, a compact automatic transmission can be achieved without making the space on the inner peripheral side of the hub member a dead space.

  According to the invention of claim 6, the bottom portion of the rotating member includes the first wall portion on the radially inner peripheral side of the punching hole, and the hub member is pivoted across both axial sides of the first wall portion. Since it extends in the direction, the inclined surface having the draft angle described above makes it possible to reliably supply oil to a portion opposite to the end of the hub member where oil cannot be directly supplied from the oil supply means. As a result, the axial dimension of the rotating member including the hub member can be reduced without affecting the lubricating action on the frictional engagement element.

  According to the invention which concerns on Claim 7, the discharge hole which discharges the oil which flowed in in the rotating member through the die-cutting hole to the exterior of the said rotating member is opened in the radial direction on the outer peripheral wall of the rotating member. Therefore, the oil supplied to the inner periphery of the hub member can be easily discharged to the outside of the rotating member through the die cutting hole and the discharge hole, and a smooth flow of oil can be realized.

  According to the eighth aspect of the invention, the oil supply means has the guide member provided with the guide portion that guides the lubricating oil supplied from the oil supply source toward the inner periphery of the hub member. By supplying the lubricating oil at the boundary between the first inclined surface (inclination toward the front side) and the second inclined surface (inclination toward the rear side) by the member, the lubricating oil is evenly supplied to the entire friction element. be able to.

  According to the ninth aspect of the present invention, the inner peripheral surface of the hub member has a first inclined surface that is inclined in a direction in which the diameter increases from the predetermined position away from the punching hole toward the opening direction of the rotating member. Since the second inclined surface is inclined in a direction in which the diameter increases from the predetermined position toward the direction opposite to the opening direction of the rotating member, the first inclined surface and the second inclined surface are provided by the guide member. By supplying the lubricating oil at the boundary, the lubricating oil can be supplied uniformly to the entire friction element.

  According to the invention which concerns on Claim 10, while forming the 1st inclined surface inclined in the direction which a diameter spreads in the inner periphery of a hub member toward the opening direction of a rotation member, the rotation member in the axial direction of a hub member Since the protruding dam is integrally formed on the inner periphery of the terminal portion in the direction opposite to the opening direction, the oil retaining action on the inner periphery of the hub member can be enhanced by the dam.

  According to the eleventh aspect of the present invention, one of the first and second molds that form the cavity for forming the rotary member penetrates the cavity portion forming the bottom wall and opens the rotary member on the inner periphery of the hub member. Since it has the 1st die part for die cutting which molds the 1st inclined surface inclined in the direction which a diameter spreads toward the direction, it is a diameter as it goes to the opening direction of a rotating member at the time of die-casting of a rotating member. The first inclined surface inclined in the direction in which the angle spreads can be simultaneously formed. Accordingly, it is not necessary to increase the number of manufacturing steps in order to form the inclined surface, and the friction engagement element can be accurately lubricated without increasing the cost.

  According to the twelfth aspect of the present invention, the other of the first and second molds is brought into contact with the first mold portion at a predetermined position away from the cavity portion forming the bottom wall to be in the inner periphery of the hub member. Since it has the 2nd mold part which simultaneously molds the 2nd inclined surface opposite to the 1st inclined surface, the 1st inclined surface and the 2nd inclined surface in consideration of the balance of the whole lubrication to the inner circumference of the hub member The degree of freedom of design can be increased.

  According to the invention of claim 13, a gap is provided between the tip of the first mold part of the first mold and the second mold, and the weir is simultaneously formed on the inner periphery of the hub member by this gap. Since it did in this way, the holding | maintenance effect | action of the oil to the inner periphery of a hub member can be improved, without increasing the special process for forming a weir or the number of parts.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 2 shows an automatic transmission 10 suitable for use in, for example, a front engine rear drive type vehicle. The automatic transmission 10 includes a torque converter 12 and a transmission 13 in a transmission case 11 attached to a vehicle body. The torque converter 12 is connected to a drive shaft 14 that is connected to a drive shaft 14 that outputs the rotation of the engine (not shown), and is connected to an input shaft 16 that is rotated in accordance with the rotation of the pump impeller 15 and inputs the rotation to the transmission 13. Turbine runner 17, stator 19 mounted on one-way clutch 18, lockup clutch 20 that is engaged when a predetermined condition is established and connects drive shaft 14 and input shaft 16. Yes. The transmission 13 shifts the rotation input from the input shaft 16 and outputs it to the output shaft 21 connected to the drive wheels.

  The input shaft 16 and the output shaft 21 of the automatic transmission 10 are coaxial with respect to the traveling direction of the vehicle. The torque converter 12 is disposed on the front side with respect to the traveling direction of the vehicle, and the output shaft 21 is disposed on the rear side with respect to the traveling direction of the vehicle. In the present embodiment, the torque converter 12 side (front side in the vehicle traveling direction) in the axial direction of the automatic transmission 10 is referred to as “front”, and the output shaft 21 side (rear side in the vehicle traveling direction) is referred to as “rear”. .

  The transmission 13 includes an input shaft 16 that is sequentially supported coaxially within the transmission case 11, a planetary gear for reduction 25, a planetary gear set 26 including a plurality of planetary gears, an output shaft 21, and a first frictional engagement element. Or it is comprised by 3rd clutch C1-C3 and 1st and 2nd brake B1, B2.

  A reduction planetary gear 25 that reduces the rotation of the input shaft 16 and transmits the rotation to the planetary gear set 26 is a sun gear S1 that is always fixed to the transmission case 11 and restricted in rotation, a ring gear R1 that is directly connected to the input shaft 16, It is constituted by a carrier CR1 that supports a sun gear S1 and a pinion P1 that meshes with the ring gear R1.

  As an example, the planetary gear set 26 is configured by a Ravigneaux type gear set in which a single pinion planetary gear and a double pinion planetary gear are combined.

  The first sun gear S2 having a small diameter of the planetary gear set 26 is detachably connected to the carrier CR1 of the planetary gear for reduction 25 by the first clutch C1, and the second sun gear S3 having a large diameter is transmitted by the first brake B1. The case 11 is detachably connected to the case 11 and is detachably connected to the carrier CR1 of the speed reduction planetary gear 25 by the third clutch C3. A short pinion P2 is meshed with the first sun gear S2, a long pinion P3 is meshed with the second sun gear S3, and the short pinion P2 and the long pinion P3 are meshed with each other. The short pinion P2 and the long pinion P3 are rotatably supported by a carrier CR2 having a direct connection structure. The ring gear R2 meshes with the long pinion P3 and is connected to the output shaft 21 as an output element.

  The carrier CR2 is detachably connected to the input shaft 16 by the second clutch C2. Further, the carrier CR2 is detachably connected to the transmission case 11 by the second brake B2, and the rotation in one direction is restricted by the one-way clutch F1 disposed in parallel to the second brake B2.

  The automatic transmission 10 configured as described above selectively disengages the first to third clutches C1 to C3, the first and second brakes B1 and B2, and inputs the input shaft 16, the output shaft 21, and the planetary gear for deceleration. By selectively connecting or fixing the elements of 25 and the planetary gear set 26, a gear ratio of 6 forward speeds and 1 reverse speed can be established.

  Next, the operation of the automatic transmission 10 having the above-described configuration will be described. In FIG. 3, P is the parking range, REV is the reverse range, N is the neutral range, 1ST is the first speed in the forward range, 2ND is the second speed in the forward range, 3RD is the third speed in the forward range, and 4TH is the fourth speed in the forward range. 5TH represents the fifth speed in the forward range, and 6TH represents the sixth speed in the forward range. Each range is selected by operating speed selection means such as a shift lever.

  Further, in FIG. 3, when the circles of the clutch and brake corresponding to each gear stage are marked with ○, the engagement state of the clutch and the brake is shown, and when not marked, the release state is shown.

  When the first clutch C1 is engaged at the first speed in the forward range, the input rotation is input from the input shaft 16 to the ring gear R1 of the reduction planetary gear 25, and the reduced rotation reduced by the reduction planetary gear 25 is generated by the carrier CR1. It is input to the first sun gear S2 of the planetary gear set 26 via the one clutch C1. Along with this, the rotation of the carrier CR2 is restricted by the one-way clutch F1, and as a result, the rotation reduced by the maximum reduction ratio from the ring gear R2 is output to the output shaft 21.

  When the first clutch C1 and the first brake B1 are engaged in the second speed in the forward range, the input rotation is input from the input shaft 16 to the ring gear R1 of the speed reduction planetary gear 25, and the speed reduction is reduced by the speed reduction planetary gear 25. The rotation is input from the carrier CR1 to the first sun gear S2 of the planetary gear set 26 via the first clutch C1. At this time, since the second sun gear S3 is fixed as the first brake B1 is engaged, the rotation reduced from the ring gear R2 with a reduction ratio smaller than the reduction ratio of the first speed is output to the output shaft 21. .

  Further, when the first clutch C1 and the third clutch C3 are engaged in the third speed in the forward range, the input rotation is input from the input shaft 16 to the ring gear R1 of the reduction planetary gear 25 and is decelerated by the reduction planetary gear 25. The rotation is input from the carrier CR1 to the first sun gear S2 of the planetary gear set 26 via the first clutch C1, and is input from the carrier CR1 to the second sun gear S3 via the third clutch C3, so that the planetary gear set 26 is directly connected. It becomes a state. Accordingly, the reduced rotation input to the first and second sun gears S2 and S3 is transmitted to the ring gear R2 as it is, and the rotation reduced from the ring gear R2 with a reduction ratio smaller than the reduction ratio of the second speed is output to the output shaft 21. .

  Further, when the first clutch C1 and the second clutch C2 are engaged in the fourth speed in the forward range, the input rotation is input from the input shaft 16 to the ring gear R1 of the reduction planetary gear 25 and is decelerated by the reduction planetary gear 25. The rotation is input from the carrier CR1 to the first sun gear S2 of the planetary gear set 26 via the first clutch C1, and the input rotation is input from the input shaft 16 to the carrier CR2 via the second clutch C2. Therefore, the rotation speed reduced between the rotation input to the first sun gear S2 and the rotation input to the carrier CR2 with a reduction ratio smaller than the reduction ratio of the third speed is output from the ring gear R2 to the output shaft 21. Is output.

  When the second clutch C2 and the third clutch C3 are engaged at the fifth speed in the forward range, the input rotation is input from the input shaft 16 to the ring gear R1 of the speed reduction planetary gear 25, and the speed reduction is reduced by the speed reduction planetary gear 25. The rotation is input to the second sun gear S3 of the planetary gear set 26 via the third clutch C3, and the input rotation is input from the input shaft 16 to the carrier CR2 via the second clutch C2. As a result, the rotation slightly increased with respect to the rotation of the input shaft 16 from the ring gear R2 is output to the output shaft 21.

  When the second clutch C2 and the first brake B1 are engaged at the sixth speed in the forward range, the input rotation is input from the input shaft 16 to the carrier CR2 of the planetary gear set 26 via the second clutch C2. At this time, since the second sun gear S3 is fixed as the first brake B1 is engaged, the rotation further increased with respect to the rotation of the input shaft 16 from the ring gear R2 is output to the output shaft 21.

  Further, in the reverse range, when the third clutch C3 and the second brake B2 are engaged, the input rotation is input from the input shaft 16 to the ring gear R1 of the reduction planetary gear 25, and the reduced rotation reduced by the reduction planetary gear 25 is It is input to the second sun gear S3 of the planetary gear set 26 via the third clutch C3. At this time, since the carrier CR2 is fixed with the engagement of the second brake B2, the rotation reverse to the rotation of the input shaft 16 is output from the ring gear R2 to the output shaft 21.

  Next, the main part of the automatic transmission 10 will be described. In FIG. 1, 29 is a stator shaft that extends in the axial direction of the transmission 13 and is fixed to the transmission case 11, and 30 is an oil pump. The oil pump 30 includes an oil pump body 31 fixed to the transmission case 11, an oil pump cover 32 that closes the oil pump body 31, a driven gear 33 that is rotatably fitted to the oil pump body 31, and a driven gear 33. And a drive gear 34 housed in the inner periphery of the motor.

  An impeller hub 35 integrally connected to the pump impeller 15 of the torque converter 12 is rotatably supported on the inner periphery of the oil pump body 31, and the impeller hub 35 is coupled to the drive gear 34. As a result, the drive gear 34 is rotated integrally with the impeller hub 35 by the rotation of the engine.

  A stator shaft 29 is fitted into a cylindrical portion 38 of the oil pump cover 32, and the input shaft 16 is rotatably disposed in the stator shaft 29. Further, the above-described reduction planetary gear 25 is disposed radially outward of the rear end of the stator shaft 29, and the sun gear S1 is spline-engaged with the outer periphery of the rear end of the stator shaft 29.

  A third clutch C <b> 3 is disposed outside the reduction planetary gear 25 in the radial direction. The third clutch C3 includes a friction element (friction material) 41 and a hydraulic servo 42 formed by alternately disposing an outer separate plate 39 and an inner friction plate 40.

  The hydraulic servo 42 includes a clutch drum 45 as a rotating member that is rotatably supported by a metal bush 44 with respect to the cylindrical portion 38 of the oil pump cover 32, and an annular slidably fitted in the clutch drum 45. The cancel plate 47 disposed on the piston 46 and the clutch drum 45 within the piston 46 and restricted in the rearward movement in the axial direction by the snap ring, and disposed between the piston 46 and the cancel plate 47. A spring 48 for urging 47 toward the clutch drum 45 is provided, and a cylinder oil chamber 49 is formed between the clutch drum 45 and the piston 46.

  The clutch drum 45 includes an outer peripheral wall 51 extending in the axial direction along the inner peripheral surface of the transmission case 11, an inner peripheral wall 52 extending in the axial direction along the tubular portion 38 of the oil pump cover 32, and the outer peripheral wall 51 and the inner It is formed integrally with the peripheral wall 52 and has a bottomed cylindrical shape with a bottom 53 extending substantially in the radial direction. As shown in FIG. 4, the bottom 53 extends from the front end (the left end in FIG. 1) of the inner peripheral wall 52 in the radial direction and extends rearward from the outer peripheral edge of the first wall 55. The horizontal wall portion 56 includes an inclined wall portion 58 extending obliquely rearward from the horizontal wall portion 56.

  The outer periphery of the separate plate 39 of the third clutch C3 is spline-engaged with the inner peripheral surface of the outer peripheral wall 51 of the clutch drum 45, and the inner periphery of the friction plate 40 is a connecting member connected to the carrier CR1 of the speed reduction planetary gear 25. The clutch drum 45 and the carrier CR1 of the speed reduction planetary gear 25 are connected by the spline engagement with the outer peripheral surface and the frictional engagement of the separate plate 39 and the friction plate 40 by the sliding of the piston 46. .

  An annular protrusion 61 that protrudes forward (to the left in FIG. 1) is formed on the inner peripheral edge of the bottom 53 of the clutch drum 45, and the oil pump cover 32 is formed radially outward of the protrusion 61. Adjacent to the large-diameter portion 62 of the tubular portion 38, a resin-made Zytel washer 63 is disposed.

  The cylinder oil chamber 49 of the hydraulic servo 42 has an oil passage 65 formed in the inner peripheral wall 52 of the clutch drum 45, an oil passage 66 formed in the sleeve 43, an oil passage 67 formed in the tubular portion 38 and the stator shaft 29. 68, and a hydraulic circuit provided with a hydraulic pressure regulating valve and the like, are connected to the discharge port of the oil pump 30.

  Thereby, by controlling the hydraulic pressure adjusting valve and the like, oil is supplied / discharged from / to the cylinder oil chamber 49 from the oil pump 30, the piston 46 is moved in the axial direction, and the third disposed opposite to the piston 46. The clutch C3 is disengaged.

  A first brake B1 is disposed between the clutch drum 45 and the transmission case 11, and the clutch drum 45 is connected to the transmission case by engaging the first brake B1 at the second speed and the sixth speed in the forward range. 11 is fixed. Therefore, a predetermined position of the inner diameter from the outer peripheral wall 51 in the radial direction of the bottom 53 of the clutch drum 45, in this embodiment, as shown in FIG. An annular brake hub 70 is formed as a hub member protruding toward the front. In this case, the brake hub 70 extends across both axial sides of the first wall 55 formed at the bottom 53 of the clutch drum 45. The radial position of the brake hub 70 is substantially equal to the radial position of the tip of the piston 46, and the axial position of the front end of the brake hub 70 is substantially equal to the axial position of the front end of the inner peripheral wall 52. .

  A plurality of positions in the circumferential direction of the front end surface (left end surface in FIG. 1) of the bottom portion 53 of the clutch drum 45 are extended in the radial direction, and ribs 71 are circumferential along the first wall portion 55. It is formed with a top equiangular pitch.

  As shown in FIGS. 4 and 5, between the brake hub 70 and the horizontal wall portion 56, a punching hole 73 passes through the inclined wall portion 58 from the rear (right side in FIG. 1) from the front (FIG. 1). (To the right of). A plurality of punching holes 73 are provided between the ribs 71. Specifically, two die-cutting holes 73A and 73B are formed between the ribs 71 so as to be spaced apart from each other in the circumferential direction, and the inclined wall portion 58 is formed between the two die-cutting holes 73A and 73B. Is formed (residual) in a rib shape.

  The die-cutting hole 73 has a substantially rectangular cross section perpendicular to the rotation axis of the clutch drum 45, and the substantially rectangular outer surface and inner surface in the radial direction and both sides in the circumferential direction are separated from each other after die casting. It is formed in a shape to which a gradient in which the width dimension in the radial direction and the circumferential direction are gradually increased toward the rear is provided so that the mold can be removed rearward (rightward in FIG. 1) during molding. As a result, a gradient that reduces the diameter toward a part of the inner diameter of the brake hub 70, that is, in a circumferential position corresponding to the punching hole 73 toward the front end face (left end face in FIG. 1) of the brake hub 70. The inclined surface 75 to which is given is formed.

  The first brake B <b> 1 includes a friction element (friction material) 79 formed by alternately arranging an outer separate plate 77 and an inner friction plate 78, and a hydraulic servo 80.

  The outer periphery of the separation plate 77 of the first brake B1 is spline-engaged with the inner peripheral surface of the transmission case 11, and the inner periphery of the friction plate 78 is spline-engaged with the outer peripheral surface of the brake hub 70. The friction plate 78 is frictionally engaged by the sliding of the piston 81 of the hydraulic servo 80, so that the clutch drum 45 is connected and fixed to the transmission case 11.

  Next, a configuration for lubricating the first brake B1 described above will be described. An oil groove 82 is formed in a portion adjacent to the large diameter portion 62 formed in the cylindrical portion 38 of the oil pump cover 32, and the oil groove 82 is connected to a lubricating oil supply oil passage and a hydraulic circuit (not shown). . As a result, the oil supplied from the oil pump 30 via the hydraulic circuit passes through the oil groove 82, and the front end surface of the protrusion 61 and the Zeiter washer 63 and the rear end surface (the right end surface in FIG. 1) of the large diameter portion 62. , Is supplied radially outward from the Zeiter washer 63, and supplied toward the inner peripheral surface of the brake hub 70.

  The brake hub 70 is provided with a plurality of oil holes 83 penetrating in the radial direction to supply oil supplied to the inner peripheral surface to the friction element 79 of the first brake B <b> 1. Are formed at a plurality of positions in the axial direction and the circumferential direction. A plate-like guide member 84 is sandwiched between the rear end surface of the large-diameter portion 62 of the tubular portion 38 and the front end surface of the annular washer 63. The guide member 84 is bent toward the front in the vicinity of the inner peripheral surface, and is provided with a detent locking piece 86 locked to a notch 88 formed at the upper end portion of the large-diameter portion 62, and obliquely rearward from the outer peripheral surface. And a guide portion 87 that guides the oil toward the inner peripheral surface of the brake hub 70. The oil groove 82 and the guide portion 87 of the guide member 84 constitute oil supply means for supplying oil toward the inner peripheral surface of the brake hub 70.

  In the above-described embodiment, when oil is supplied from the oil pump 30 through a lubricating oil supply oil passage and a hydraulic circuit (not shown), the oil passes through the oil groove 82, and the protrusion 61 and the annular washer 63. It passes through a gap between the front end surface and the rear end surface (the right end surface in FIG. 1) of the large-diameter portion 62 and is supplied radially outward from the Zytel washer 63. At this time, the oil is guided toward the inner peripheral surface of the brake hub 70 by the guide portion 87 of the guide member 84, and is sent to the outer peripheral surface side of the brake hub 70 through the oil hole 83 formed in the brake hub 70. The friction element 79 is lubricated.

  At this time, the inner peripheral surface of the brake hub 70 is formed with an inclined surface 75 to which a draft angle with a diameter decreasing toward the front end surface (left end surface in FIG. 1) of the brake hub 70 is formed. The oil supplied to the inner peripheral surface of the hub 70 is the rear end side (right side in FIG. 1) of the brake hub 70, that is, the inner peripheral surface of the brake hub 70 by the guide portion 87 of the guide member 84 due to the gradient of the inclined surface 75. The oil can be sufficiently supplied also to the oil hole 83 located on the rear end side of the brake hub 70 that cannot supply oil directly to the brake hub 70, and the oil can be supplied to the entire outer peripheral surface of the brake hub 70. .

  As a result, oil can be uniformly supplied to the entire friction element 79 of the first brake B1, and the friction element 79 of the first brake B1 can be accurately lubricated. Further, even if the brake hub 70 extends across both sides in the axial direction of the first wall 55 formed on the bottom 53 of the clutch drum 45, the lubrication to the first brake B1 is not hindered. The axial dimension of the clutch drum 45 including the brake hub 70 can be reduced.

  Note that the oil supplied to the inner peripheral surface of the brake hub 70 is sent to the outer peripheral surface side of the brake hub 70 from the oil hole 83, and the front end surface (the left end surface in FIG. 1) along the inner peripheral surface of the brake hub 70. ) Side and rear end face (right end face in FIG. 1) side. The oil that has flowed to the front end face side is discharged to the outside of the clutch drum 45, and the oil that has flowed to the rear end face side flows to the third clutch C3 side through the mold release hole 73. Then, the oil in the clutch drum 45 that has flowed to the third clutch C3 side is discharged to the outside of the clutch drum 45 through the discharge hole 89 formed in the outer peripheral wall 51 of the clutch drum 45, and the lower part of the transmission case 11 Through an opening 90 formed in the oil pan, the oil pan is collected in an unillustrated oil pan.

  As described above, the oil supplied to the inner peripheral surface of the brake hub 70 is distributed in the front-rear direction of the inner peripheral surface of the brake hub 70 and the outer peripheral surface side of the brake hub 70. The oil supplied to the inner peripheral surface does not flow in part, and the oil can be smoothly flowed.

  It should be noted that the formation of the punching hole 73 in the clutch drum 45 may be disadvantageous in terms of strength at that portion, but the bottom 53 of the clutch drum 45 in which the punching hole 73 is formed is provided with the hydraulic servo 42. As long as it has a function of disposing, it is a part that is not directly involved in torque transmission, and torque transmission is performed by the outer peripheral wall 51 of the clutch drum 45 and the brake hub 70, so there is no problem in strength. . Further, by forming the cylinder oil chamber 49 at a position overlapping with the brake hub 70 in the axial direction, the space on the inner peripheral side of the brake hub 70 can be made compact without making it a dead space.

  Next, a method of forming the clutch drum 45 having the above-described configuration by die casting will be described with reference to FIGS.

  Reference numerals 91 and 92 denote a pair of molds for molding the clutch drum 45, the first mold 91 defines the inner shape of the clutch drum 45, and the second mold 92 is the outer surface of the clutch drum 45. The shape is defined. The first and second molds 91 and 92 are brought into contact with each other so as to be separated from each other, and a cavity 93 for forming the clutch drum 45 is formed between the molds 91 and 92. Then, the molten metal is poured into the cavity 93, and the molten metal is cooled and solidified, whereby the clutch drum 45 is formed by die casting. Thereafter, the clutch drum 45 can be taken out by releasing the molds 91 and 92 in the X1 and X2 directions in FIG.

  The first mold 91 for defining the inner surface shape of the clutch drum 45 is a first mold for forming an inclined surface 75 whose diameter decreases toward the end of the brake hub 70 on the inner periphery of the brake hub 70. A plurality of the portions 94 are provided in a projecting manner with an interval in the circumferential direction. The first mold portion 94 is given a slight gradient that tapers toward the end of the brake hub 70 so that the first mold 91 can be removed when the mold is released after die casting. On the other hand, the second mold 92 that defines the outer shape of the clutch drum 45 has a second mold part 95 that contacts the first mold part 94 between the first mold parts 94, as shown in FIG. A plurality of protrusions are provided with intervals in the circumferential direction, and an inclined surface (not shown) whose diameter increases toward the end of the brake hub 70 is formed on the inner periphery of the brake hub 70 by the second mold portion 95. The In FIG. 7, 93A and 93B indicate cavities for forming the ribs 71 and 74 formed between the first mold part 94 and the second mold part 95, respectively.

  At the time of die casting of the clutch drum 45 described above, as shown in FIG. 6, the front end of the first mold portion 94 is extended to the end of the brake hub 70 to be die cast, that is, the first By providing the mold portion 94 over the entire axial length of the inner peripheral surface of the brake hub 70, the brake hub 70 has a circumferential portion corresponding to the die-cutting hole 73 of the brake hub 70 formed by die casting. It is possible to form the inclined surface 75 provided with a gradient that decreases in diameter toward the front end surface of the brake hub 70 over the entire axial length of the inner peripheral surface.

  Thus, according to the present embodiment, the first hub portion 94 of the first mold 91 is provided on the inner peripheral surface of the brake hub 70 without specially increasing the number of manufacturing steps. A plurality of inclined surfaces 75 to which a gradient whose diameter is reduced toward the front end surface can be formed in the circumferential direction, and an inclined surface having a gradient opposite to that can be formed between each of the inclined surfaces 75 in the circumferential direction. become.

  After the clutch drum 45 is formed by die casting as described above, the oil passage 65 is formed in the inner peripheral wall 52, the oil hole 83 is formed in the brake hub 70, the discharge hole 89 is formed in the outer peripheral wall 51, and the like by machining. Thus, the clutch drum 45 shown in FIG. 4 is completed.

  FIG. 8 shows an embodiment in which the clutch drum 45 is formed by die casting different from the method shown in FIG. 6. The tip of the first mold part 94 and the first mold part 94 As shown in FIG. 8, the contact position between the tip and the second die 92 is separated from the predetermined position in the axial direction of the inner peripheral surface of the brake hub 70 to be molded, that is, a predetermined amount away from the punching hole 73. The predetermined position P1 is set. According to this, the brake hub 70 formed by die casting is connected to the predetermined position P1 in the axial direction of the inner peripheral surface of the circumferential portion corresponding to the punching hole 73 from the position P1. An inclination in which the diameter of the clutch drum 45 is reduced toward the first inclined surface 75A, that is, the front end surface of the brake hub 70, is provided by the first mold portion 94 on the opening direction side (right direction in FIG. 1). A surface 75A is formed, and on the side opposite to the opening direction of the clutch drum 45 from the position P1 (left direction in FIG. 1), there is a first inclined surface 75A for releasing the second mold 92. The second inclined surface 75B having the reverse gradient is formed at the same time.

  According to this, the first and second inclined surfaces 75A and 75B having opposite gradients in the axial direction of the brake hub 70 can be simultaneously formed, and the ratio of the lengths of the first inclined surface 75A and the second inclined surface 75B. Can be set arbitrarily.

  Further, as shown in FIG. 9, the tip of the first mold part 94 extends slightly to the front of the end part of the brake hub 70 so that a slight gap is provided between the first mold part 94 and the second mold 92. Thus, a protruding dam 97 can be formed between the tip of the first mold portion 94 of the first mold 91 and the second mold 92.

  According to this, the weir 97 can be formed simultaneously with the above-described inclined surface 75 at the time of die casting of the clutch drum 45, and the clutch hub 70 can be formed without increasing the number of steps or the number of parts for forming the weir 97. It becomes possible to enhance the action of retaining oil on the inner peripheral surface.

  The position of the tip of the first mold portion 94 is determined depending on the number of the friction elements 79, the oil supply portion to the inner periphery of the brake hub 70 by the guide portion 87 of the guide member 84, and the first brake C1. The amount of oil supplied to the friction element 79 can be arbitrarily set in consideration of the balance of the entire lubrication, thereby enabling optimum lubrication of the first brake C1.

  In the above-described embodiment, the bottom portion 53 of the clutch drum 45 includes the first wall portion 55 extending in the radial direction from the front end of the inner peripheral wall 52 and the horizontal wall portion extending rearward from the outer peripheral edge portion of the first wall portion 55. 56, the bottom wall 53 can basically connect the outer peripheral wall 51 and the inner peripheral wall 52, and the cylinder oil chamber 49 of the hydraulic servo 42. Can be formed on the radially inner peripheral side of the punching hole 73, and is not limited to the embodiment.

  In the above embodiment, the brake hub 70 as the hub member is formed on the clutch drum 45 as the rotating member. However, in order to selectively fix the clutch drum to the other rotating members, A clutch can be provided between the drum and another rotating member. In this case, a clutch hub as a hub member may be formed on the clutch drum 45, and the hub member is specified for a brake or a clutch. Is not to be done.

  Thus, the specific configuration described in the above embodiment is merely an example of the present invention, and the present invention is not limited to such a specific configuration. Of course, various embodiments can be employed without departing from the scope.

It is principal part sectional drawing of the automatic transmission which shows embodiment of this invention. It is a conceptual diagram of the automatic transmission in embodiment of this invention. FIG. 3 is a diagram illustrating engagement states of a brake and a clutch at each gear stage of the automatic transmission in FIG. 2. It is sectional drawing which shows a clutch drum. FIG. 5 is a view taken in the direction of arrow 5 in FIG. 4. It is a figure which shows the manufacturing method of a clutch drum. It is sectional drawing cut | disconnected along the 7-7 line | wire of FIG. It is a figure which shows another manufacturing method of a clutch drum. It is a figure which shows another manufacturing method of a clutch drum.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Automatic transmission, 11 ... Transmission case, 12 ... Torque converter, 13 ... Transmission device, 16 ... Input shaft, 21 ... Output shaft, 35, 79 ... Friction element, 36 ... hydraulic servo, 45 ... rotating member (clutch drum), 41 ... piston, 44 ... cylinder oil chamber, 51 ... outer peripheral wall, 52 ... inner peripheral wall, 53 ... Bottom, 55 ... First wall, 56 ... Horizontal wall, 58 ... Inclined wall, 65-67 ... Oil passage, 70 ... Hub member (brake hub), 71, 74 ... ribs, 73 ... punching holes, 75 ... inclined surfaces, 82 ... oil grooves, 83 ... oil holes, 84 ... guide members, 87 ... guides 89, discharge hole, 91, 92 ... mold, 93 ... cavity, 94 ... first mold part, 95 ... second mold part, 1~C3 ··· clutch, B1, B2 ··· brake.

Claims (13)

In an automatic transmission including a transmission having a plurality of friction engagement elements including a clutch and a brake, the transmission having a bottomed cylindrical rotating member formed by die casting,
The rotating member has a hub member that extends in a direction opposite to the opening direction of the rotating member from the bottom of the rotating member and that splines engages the friction element of the friction engaging element on the outer periphery.
The hub member is disposed so as to at least partially overlap the bottom of the rotating member in the axial direction,
An automatic transmission characterized in that at least a part of the draft angle in the circumferential direction of the inner circumference of the hub member is inclined in a direction in which the diameter increases as it goes in the opening direction of the rotating member. In Claim 1, The said transmission has an oil supply means which supplies the lubricating oil which lubricates the said friction element to the radial direction inner peripheral side of the said hub member,
The automatic transmission according to claim 1, wherein the hub member has at least one oil hole for supplying the lubricating oil supplied from the oil supply means to the friction element.   3. The hub according to claim 1, wherein a plurality of die-cutting holes are formed on the bottom of the rotating member on the circumference in a die-cast casting that penetrates in the axial direction, and the hub corresponds to the die-cutting holes. An automatic transmission characterized in that an inclined surface that is inclined in a direction in which a diameter increases as it goes in an opening direction of the rotating member is formed in a part of a circumferential direction of an inner periphery of the member.   4. The automatic transmission according to claim 3, wherein torque transmission is not performed on an inner peripheral side of the punching hole at the bottom of the rotating member.   The rotary member according to claim 4, wherein the rotating member is a clutch drum that forms a hydraulic servo of a clutch that is one of the plurality of friction engagement elements, and the clutch drum has an inner diameter in the radial direction of the die-cutting hole. An automatic transmission characterized in that a cylinder oil chamber of the hydraulic servo is formed on a circumferential side.   6. The rotary member according to claim 3, wherein the rotating member has an outer peripheral wall and an inner peripheral wall extending in an axial direction from the bottom portion, and the bottom portion is a radially inner peripheral side of the die-cutting hole. The automatic transmission has a first wall portion, and the hub member extends on both sides of the first wall portion in the axial direction on the outer peripheral side of the first wall portion.   In Claim 6, The discharge hole which discharges the oil which flowed in in the said rotation member via the said punching hole to the exterior of the said rotation member is opened in the outer peripheral wall of the said rotation member in the radial direction. Automatic transmission characterized by.   8. The oil supply means according to claim 2, wherein the oil supply means includes a guide member including a guide portion that guides the lubricating oil supplied from the oil supply source toward the inner periphery of the hub member. An automatic transmission characterized by   In Claim 8, the inner peripheral surface of the hub member is a first inclined surface inclined in a direction in which the diameter increases from the predetermined position away from the punching hole toward the opening direction of the rotating member, An automatic transmission comprising: a second inclined surface that is inclined in a direction in which a diameter increases from a predetermined position toward a direction opposite to an opening direction of the rotating member.   9. The hub according to claim 1, wherein a first inclined surface that is inclined in a direction in which a diameter is increased toward an opening direction of the rotating member is formed on an inner periphery of the hub member, and the hub is formed. An automatic transmission characterized in that a protruding weir is integrally formed on the inner periphery of a terminal portion in the direction opposite to the opening direction of the rotating member in the axial direction of the member. In an automatic transmission including a transmission having a plurality of friction engagement elements including a clutch and a brake, the transmission having a bottomed cylindrical rotating member formed by die casting,
The rotating member molding comprising: an outer peripheral wall extending in the axial direction; an inner peripheral wall extending in the axial direction; a bottom wall connecting the outer peripheral wall and the inner peripheral wall; and a hub member extending from the bottom wall in a direction opposite to the outer peripheral wall. A first mold and a second mold for forming a cavity for use, and one of the first mold and the second mold passes through the cavity portion forming the bottom wall and is arranged on the inner periphery of the hub member. A method for producing a rotating member, comprising: a first die part for die cutting that molds a first inclined surface that is inclined in a direction in which a diameter is increased in a direction toward the opening of the first member.   12. The other of the first and second molds according to claim 11, wherein the first mold part is brought into contact with the first mold part at a predetermined position away from the cavity part forming the bottom wall, and is brought into contact with the inner periphery of the hub member. A method of manufacturing a rotating member, comprising: a second mold part that simultaneously molds a second inclined surface having a reverse gradient to the first inclined surface.   In Claim 11, the clearance gap was provided between the front-end | tip part of the said 1st mold part of the said 1st metal mold | die, and the said 2nd metal mold | die, and the weir was simultaneously shape | molded by the clearance gap in the inner periphery of the said hub member. The manufacturing method of the rotating member characterized by these.

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