JP2013155849A - Transmission - Google Patents

Transmission Download PDF

Info

Publication number
JP2013155849A
JP2013155849A JP2012018718A JP2012018718A JP2013155849A JP 2013155849 A JP2013155849 A JP 2013155849A JP 2012018718 A JP2012018718 A JP 2012018718A JP 2012018718 A JP2012018718 A JP 2012018718A JP 2013155849 A JP2013155849 A JP 2013155849A
Authority
JP
Japan
Prior art keywords
drum
clutch
portion
drum member
formed
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2012018718A
Other languages
Japanese (ja)
Other versions
JP5919850B2 (en
Inventor
Satoru Kasuya
悟 糟谷
Hiroshi Kato
博 加藤
Toshihiko Aoki
敏彦 青木
Michio Nobata
道夫 野畑
Norihiro Tokunaga
憲洋 徳永
Masato Nakamura
真人 中村
Hiroshi Matsushima
寛 松嶋
Original Assignee
Aisin Aw Co Ltd
アイシン・エィ・ダブリュ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Aisin Aw Co Ltd, アイシン・エィ・ダブリュ株式会社 filed Critical Aisin Aw Co Ltd
Priority to JP2012018718A priority Critical patent/JP5919850B2/en
Publication of JP2013155849A publication Critical patent/JP2013155849A/en
Application granted granted Critical
Publication of JP5919850B2 publication Critical patent/JP5919850B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

PROBLEM TO BE SOLVED: To allow a drum member to be a rotation detection object to be detected by a rotation sensor while suppressing deformation of the drum member doubling as a clutch drum and a band brake drum.SOLUTION: An automatic transmission 25 includes: a bottomed cylindrical drum member 11 doubling as a clutch drum and a band brake drum; and a rotation sensor 200 detecting rotation of the drum member 11. An outer drum 15 of the drum member 11 is formed by flow forming so that on a side of an inner periphery, a spline 151 to which a clutch plate 403 of a clutch C3 is fitted is provided, and on a side of an outer periphery, an engagement surface 152 fastened by a brake band 10 is provided. On an outer peripheral surface of the outer drum 15, a recessed portion 155 to be a portion to be detected by the rotation sensor 200 is formed to be positioned closer to a side of an opening end surface 15o than the engagement surface 152 without being opened in the opening end surface 15o.

Description

  The present invention relates to a transmission including a bottomed cylindrical drum member that is also used as a clutch drum and a band brake drum, and a rotation sensor that detects rotation of the drum member.

  2. Description of the Related Art Conventionally, as a drum member included in this type of transmission, an integrated drum having a first drum portion with internal teeth, a second drum portion with external teeth, and a boss portion are known. (For example, refer to Patent Document 1). When manufacturing this integrated drum, the axial center of the mandrel (die) and the pressure plate is aligned and the boss of a single circular plate is clamped and fixed while cold plastic deformation by flow forming is used. Inner teeth are formed on the inner surface of the first drum portion, and outer teeth are formed on the outer surface of the second drum portion by cold plastic deformation by rolling. Further, as this kind of drum member, there is also known a drum member having an uneven surface, a color pattern, a notch or a hole on the outer peripheral surface which becomes a detected portion of a rotation sensor arranged on the outer peripheral side (for example, Patent Document 2). And 3).

JP-A-10-296365 Japanese Patent Laid-Open No. 04-175545 JP 2001-173761 A

  As described in Patent Document 1, by using flow forming, a drum member that is also used as a clutch drum and a band brake drum can be molded with high accuracy and high strength. And by forming a recessed part in the outer peripheral surface of the drum member shape | molded by flow forming, the said drum member can be made into the rotation detection object of a rotation sensor. However, since flow forming is to compress a material by applying a high pressing force to the material via a roller or the like, a drum formed at least partially by flow forming is caused by residual stress after flow forming. It has the characteristic of spreading outward. Therefore, depending on the form of formation of the concave portion that becomes the detected portion of the rotation sensor, the drum member may be distorted or deformed on the outer periphery, thereby reducing or destabilizing the braking performance of the band brake including the drum member. There is.

  Therefore, the main purpose of the transmission according to the present invention is to suppress the deformation of a drum member that is also used as a clutch drum and a band brake drum, and to make the drum member an object of rotation detection by a rotation sensor.

  The transmission according to the present invention adopts the following means in order to achieve the main object.

A transmission according to the present invention includes:
In a transmission including a bottomed cylindrical drum member that is also used as a clutch drum and a band brake drum, and a rotation sensor that detects rotation of the drum member,
At least the cylindrical portion of the drum member is formed by flow forming so as to have a spline to which a clutch plate of a clutch is fitted on the inner peripheral side and an engagement surface tightened by a brake band on the outer peripheral side,
On the outer peripheral surface of the cylindrical portion, a recess serving as a detected portion of the rotation sensor is formed so as to be positioned closer to the opening end surface than the engagement surface without opening at the opening end surface of the cylindrical portion. It is characterized by that.

  At least the cylindrical portion of the drum member included in the transmission is formed by flow forming so that the spline to which the clutch plate of the clutch is fitted is provided on the inner peripheral side and the engagement surface to be tightened by the brake band is provided on the outer peripheral side. Is done. And the concave part which becomes a to-be-detected part of a rotation sensor is formed in the outer peripheral surface of a cylindrical part so that it may be located in the opening end face side rather than an engagement face, without opening at the opening end face of the said cylindrical part, The end on the opening end face side is located closer to the engaging face than the opening end face. In this way, by forming the concave portion that becomes the detected portion of the rotation sensor so as not to open at the opening end surface of the cylindrical portion, there is no dent to release the residual stress after flow forming in the vicinity of the opening end surface of the cylindrical portion. Since the balance of stress in the vicinity of the end surface is maintained, the drum member can be prevented from being deformed so that the opening end surface side is widened. Therefore, in this transmission, it is possible to make the drum member a rotation detection target by the rotation sensor while suppressing deformation of the cylindrical portion formed to function as both the clutch drum and the band brake drum by flow forming. Become.

  Moreover, the thickness of the part of the cylindrical part closer to the opening end surface than the concave part may be thicker than the thickness of the part of the cylindrical part forming the bottom part of the concave part. Thereby, it becomes possible to prevent the formation of a recess for releasing the residual stress after the flow forming in the vicinity of the opening end face of the cylindrical portion.

  Furthermore, a plurality of the recesses may be formed on the outer peripheral surface at intervals in the circumferential direction so as to be positioned on the back side of the teeth of the spline, and the number of the recesses may be smaller than the number of teeth of the spline. . In this way, it is possible to better suppress the deformation of the drum member by not increasing the number of recesses that are to be detected by the rotation sensor more than necessary.

  Further, the drum member may be rotatably supported only at one place on the inner peripheral side. That is, the drum member that is rotatably supported by one bearing may rotate while being swung (tilted) with the support portion supported by the bearing as a fulcrum. In a band brake including the drum member, The influence of deformation of the cylindrical portion tends to appear on the braking performance and the like. Therefore, forming the concave portion as the detected portion in the cylindrical portion so as not to open at the opening end surface and suppressing the deformation of the cylindrical portion means that at least the cylindrical portion is formed by flow forming and rotated by one bearing. This is extremely useful for suppressing a reduction in the braking performance of a band brake including a drum member that is freely supported.

  Furthermore, a planetary gear mechanism and a second clutch different from the clutch may be arranged in the axial direction inside the drum member. As described above, when the planetary gear mechanism and the second clutch are arranged in the axial direction at least inside the drum member in which the cylindrical portion is formed by flow forming, the end of the cylindrical portion on the opening side is increased by increasing the axial length. The part is likely to spread outward. Therefore, forming the concave portion as the detected portion in the cylindrical portion so as not to open at the opening end surface suppresses deformation of the drum member having the cylindrical portion formed by flow forming and having various elements disposed therein. It is extremely useful in doing so.

  The second clutch may include a second clutch drum to which a second clutch plate is fitted, and the second clutch drum is interposed via a fastening member extending in the axial direction of the cylindrical portion. The drum member may be fastened. As described above, when the second clutch drum of the second clutch is fastened to the drum member by the fastening member, the second clutch drum is compared with the case where the second clutch drum is fixed to the drum member using a snap ring or the like. It is possible to reduce the axial length required for fixing the. However, when the second clutch drum is fastened to the drum member by the fastening member extending in the axial direction of the cylindrical portion, the end on the opening side of the drum member is easily spread outward due to a load for fastening the fastening member. Therefore, forming the concave portion as the detected portion in the cylindrical portion so as not to open at the opening end surface suppresses deformation of the drum member that has the cylindrical portion formed by flow forming and to which the second clutch drum is fastened. Very useful above.

  Further, the drum member may include a side wall portion extending in a radial direction and having a base end portion of the cylindrical portion fixed to an outer periphery thereof, and the second clutch is at least viewed from a radial direction on an inner peripheral side of the clutch. A part may be arranged so as to overlap the clutch, and an oil passage communicating with the oil chamber of the clutch may be formed in the side wall portion. Thus, when the oil passage is formed in the side wall portion of the drum member, it is difficult to integrally form the cylindrical portion and the side wall portion by flow forming, and it is preferable to fix the cylindrical portion to the separate side wall portion. However, when the cylindrical portion formed by flow forming is fixed to the side wall portion, the alignment accuracy of the cylindrical portion may be slightly lowered as compared with the case where the entire drum member is integrally formed. In the brake, the influence of the deformation of the cylindrical portion tends to appear on the braking performance or the like. Therefore, forming the concave portion as the detected portion in the cylindrical portion so as not to open at the opening end surface and suppressing the deformation of the cylindrical portion includes the cylindrical portion formed by flow forming and fixed to the side wall portion. This is extremely useful for suppressing a decrease in the braking performance of the band brake including the drum member.

It is a schematic block diagram of the power transmission device 20 provided with the automatic transmission 25 which concerns on one Example of this invention. 3 is an operation table showing a relationship between each gear position of the automatic transmission 25 and operation states of clutches and brakes. FIG. 2 is an enlarged partial cross-sectional view showing a main part of an automatic transmission 25. FIG. 2 is an enlarged partial cross-sectional view showing a main part of an automatic transmission 25. It is the front view which looked at the outer drum 15 of the drum member 11 contained in the automatic transmission 25 from the opening end surface 15o side. It is a schematic diagram which illustrates the deformation | transformation aspect of the outer drum 15 at the time of opening the recessed part 155 by the opening end surface 15o. 3 is an enlarged view of a main part showing an outer drum 15. FIG. It is sectional drawing along the VIII-VIII line in FIG.

  Next, the form for implementing this invention is demonstrated using an Example.

  FIG. 1 is a schematic configuration diagram of a power transmission device 20 including an automatic transmission 25 according to an embodiment of the present invention. A power transmission device 20 shown in the figure is connected to a crankshaft of an engine (not shown) mounted on a vehicle and transmits power from the engine to left and right drive wheels (not shown). A torque converter 23, an oil pump 24, an automatic transmission 25, a differential mechanism (differential gear) 29, and the like housed in the transmission case 22 are provided.

  The torque converter 23 is disposed inside the input-side pump impeller 23p connected to the crankshaft of the engine, the output-side turbine runner 23t, the pump impeller 23p, and the turbine runner 23t connected to the input shaft 26 of the automatic transmission 25. It includes a stator 23s that is arranged to rectify the flow of hydraulic oil from the turbine runner 23t to the pump impeller 23p, a one-way clutch 23o that restricts the rotational direction of the stator 23s in one direction, a lock-up clutch 23c, and the like. The oil pump 24 is configured as a gear pump including a pump assembly including a pump body and a pump cover, and an external gear connected to a pump impeller 23p of the torque converter 23 via a hub. The oil pump 24 is driven by power from the engine, sucks hydraulic oil (ATF) stored in an oil pan (not shown), and pumps it to a hydraulic control device (not shown).

  The automatic transmission 25 is configured as an eight-speed transmission, and as shown in FIG. 1, in addition to the input shaft 26 and the output shaft 27, a double pinion type first planetary gear mechanism 30 and a Ravigneaux Second planetary gear mechanism 35, four clutches C1, C2, C3 and C4 for changing the power transmission path from the input side to the output side, two brakes B1 and B2, and a one-way clutch F1 . The output shaft 27 of the automatic transmission 25 is formed in a hollow shape and is connected to drive wheels (not shown) via a gear mechanism 28 and a differential mechanism 29.

  The first planetary gear mechanism 30 includes a sun gear 31 that is an external gear, a ring gear 32 that is an internal gear disposed concentrically with the sun gear 31, and one of the sun gear 31 and the other is a ring gear 32. It has a planetary carrier 34 that holds a plurality of meshing pairs of pinion gears 33a and 33b so as to rotate and revolve. As shown in the drawing, the sun gear 31 of the first planetary gear mechanism 30 is fixed to the transmission case 22, and the planetary carrier 34 of the first planetary gear mechanism 30 is connected to the input shaft 26 so as to be integrally rotatable. The first planetary gear mechanism 30 is configured as a so-called reduction gear, and decelerates the power transmitted to the planetary carrier 34 as an input element and outputs it from the ring gear 32 as an output element.

  The second planetary gear mechanism 35 includes a first sun gear 36a and a second sun gear 36b which are external gears, a ring gear 37 which is an internal gear disposed concentrically with the first and second sun gears 36a and 36b, A plurality of short pinion gears 38a meshing with one sun gear 36a, a plurality of long pinion gears 38b meshing with the second sun gear 36b and the plurality of short pinion gears 38a and meshing with the ring gear 37, a plurality of short pinion gears 38a and a plurality of long pinion gears 38b And a planetary carrier 39 that holds the motor in a rotatable (rotatable) and revolving manner. The ring gear 37 of the second planetary gear mechanism 35 is connected to the output shaft 27, and the planetary carrier 39 of the second planetary gear mechanism 35 is supported by the transmission case 22 via the one-way clutch F1.

  The clutch C1 is a hydraulic clutch (friction engagement element) that can fasten the ring gear 32 of the first planetary gear mechanism 30 and the first sun gear 36a of the second planetary gear mechanism 35 and release the fastening of both. The clutch C2 is a hydraulic clutch that can fasten the input shaft 26 and the planetary carrier 39 of the second planetary gear mechanism 35 and release the fastening of both. The clutch C3 is a hydraulic clutch that can fasten the ring gear 32 of the first planetary gear mechanism 30 and the second sun gear 36b of the second planetary gear mechanism 35 and release the fastening of both. The clutch C4 is a hydraulic clutch that can fasten the planetary carrier 34 of the first planetary gear mechanism 30 and the second sun gear 36b of the second planetary gear mechanism 35 and release the fastening of both. The brake B1 is a hydraulic brake (friction engagement element) capable of fixing the second sun gear 36b of the second planetary gear mechanism 35 to the transmission case 22 so as not to rotate and releasing the fixing of the second sun gear 36b to the transmission case 22. It is. The brake B2 is a hydraulic brake that can fix the planetary carrier 39 of the second planetary gear mechanism 35 to the transmission case 22 in a non-rotatable manner and can release the fixation of the planetary carrier 39 to the transmission case 22.

  The clutches C1 to C4 and the brakes B1 and B2 operate by receiving and supplying hydraulic oil from a hydraulic control device (not shown). FIG. 2 shows an operation table showing the relationship between the respective speeds of the automatic transmission 25 and the operating states of the clutches C1 to C4, the brakes B1 and B2, and the one-way clutch F1. The automatic transmission 25 provides the forward 1st to 8th gears and the reverse 1st and 2nd gears by setting the clutches C1 to C4 and the brakes B1 and B2 to the states shown in the operation table of FIG. .

  3 and 4 are enlarged partial cross-sectional views of the main part showing the automatic transmission 25. As shown in the figure, the clutches C1, C3 and C4 of the automatic transmission 25 are all configured as multi-plate friction hydraulic clutches. The brake B1 is configured as a band brake including a brake band 10 having one end fixed to the transmission case 22 and the other end pressed by a hydraulic actuator (not shown). The automatic transmission 25 includes a bottomed cylindrical drum member 11 that is also used as a clutch drum of the clutch C3 (first clutch) and a band brake drum of the brake B1, and the clutches C1, C3 are disposed inside the drum member 11. And C4, and the first planetary gear mechanism 30 are arranged. That is, inside the drum member 11, the clutch C4 (second clutch), the first planetary gear mechanism 30, and the clutch C1 (third clutch) are arranged in this order from the engine side (right side in the figure) (not shown) in this order. Arranged in the axial direction of the (drum member 11), the clutch C3 is arranged on the outer peripheral side of the clutch C4. In addition, the brake band 10 of an Example has what is called a double winding structure so that it may show in figure.

  The drum member 11 includes an inner drum 12 and an outer drum (cylindrical portion) 15 fixed to the outer periphery of the inner drum 12. The inner drum 12 is formed by cutting a metal material. The inner drum 12 extends in the axial direction of the automatic transmission 25, and one end of the inner cylinder 121 (the right end in the figure). And an annular side wall 122 extending radially outward. The inner cylinder portion 121 of the inner drum 12 is integrated with the transmission case 22 and is rotatable via a sleeve 13 on a hollow fixed shaft portion 22a that extends in parallel with the input shaft 26 on the outer peripheral side of the input shaft 26. And one radial bearing 90 is disposed between the free end portion (left end portion in the figure) of the inner cylinder portion 121 and the fixed shaft portion 22a. Thereby, the drum member 11 is rotatably supported with respect to the transmission case 22 by the radial bearing 90. Further, from the side wall portion 122 of the inner drum 12, a short cylindrical fixing portion 123 is extended inward in the axial direction (left side in the drawing) so as to be positioned between the inner cylinder portion 121 and the outer drum 15. Yes.

  The outer drum 15 of the drum member 11 has a spline 151 on the inner peripheral side and an outer peripheral side by flow forming in which a circular metal plate is pressed with a roller while rotating a metal mold having a spline forming tooth mold on the outer periphery. The cylindrical engagement surface 152 is fastened by the brake band 10. By utilizing such flow forming, the relatively long outer drum 15 in which the clutches C1, C3, C4 and the first planetary gear mechanism 30 are arranged can be formed with high accuracy and high strength. . Further, the engagement surface 152 has an axial length longer than the maximum width of the brake band 10, and the engagement surface 152 is smoothed after the flow forming process. Furthermore, the base end portion 15p (see FIG. 4) of the outer drum 15 extends radially inward and is fixed to the outer periphery of the side wall portion 122 of the inner drum 12 by welding. As shown in the figure, the outer drum 15 is connected to the second sun gear 36b of the second planetary gear mechanism 35 via the connecting member 16 fitted to the spline 151 in the vicinity of the opening end thereof so as to be integrally rotatable. .

  The clutch C1 includes a clutch drum 101 coupled to the first sun gear 36a of the second planetary gear mechanism 35 via the coupling member 100, a clutch hub 102 integrated with the ring gear 32 of the first planetary gear mechanism 30, A plurality of annular clutch plates (mating plates) 103 fitted to splines formed on the inner peripheral surface of the drum 101, and a plurality of annular clutches fitted to splines formed on the outer peripheral surface of the clutch hub 102 A plate (friction plate) 104 and a clutch piston 105 capable of pressing the clutch plates 103 and 104 are included. The clutch piston 105 is slidably fitted into a cylindrical portion 100 a formed on the connecting member 100, and defines an engagement side oil chamber 106 together with the connecting member 100. Further, a cancel plate 107 is fixed to the tubular portion 100 a of the connecting member 100 so as to be positioned on the engine side (right side in the drawing) with respect to the clutch piston 105. The cancel plate 107 defines a cancel oil chamber 108 for canceling centrifugal oil pressure generated in the engagement side oil chamber 106 together with the clutch piston 105, and a return spring is interposed between the clutch piston 105 and the cancel plate 107. 109 is arranged.

  The clutch C3 uses the above-described drum member 11 as a clutch drum, and also uses the clutch hub 102 integrated with the ring gear 32 of the first planetary gear mechanism 30 also as the clutch C3. The clutch C3 is fitted to a plurality of annular clutch plates (mating plates) 303 fitted to the splines 151 formed on the inner peripheral surface of the outer drum 15 of the drum member 11 and the splines of the clutch hub 102. A plurality of annular clutch plates (friction plates) 304 and a clutch piston 305 capable of pressing the clutch plates 303 and 304. The clutch piston 305 is slidably fitted to the outer periphery of the fixed portion 123 formed on the side wall portion 122 of the inner drum 12 and engages with the spline 151 formed on the inner periphery of the outer drum 15. An engagement side oil chamber 306 is defined together with the drum 12 and the outer drum 15.

  Further, a cancel plate 307 is fixed to the fixing portion 123 formed on the side wall portion 122 of the drum member 11 so as to be positioned on the clutch C1 side (left side in the drawing) with respect to the clutch piston 305. The cancel plate 307 defines a cancel oil chamber 308 for canceling centrifugal oil pressure generated in the engagement side oil chamber 306 together with the clutch piston 305, and a return spring is interposed between the clutch piston 305 and the cancel plate 307. 309 is arranged. In the automatic transmission 25 of the embodiment, a cylindrical aligning portion 123 a (see FIG. 4) extends inward in the axial direction from the inner peripheral side of the free end portion of the fixed portion 123. The peripheral portion is fitted to the outer periphery of the aligning portion 123a. The cancel plate 307 is fastened to the fixed portion 123 via the rivet 14 extending in the axial direction of the automatic transmission 25 (drum member 11). Further, a seal member is disposed between the outer periphery of the cancel plate 307 and the clutch piston 305.

  As shown in FIGS. 3 and 4, the clutch C4 is disposed inside the clutch C3 so that at least a part thereof overlaps the clutch C3 when viewed from the radial direction. The clutch C4 is a clutch hub 401 integrated with the clutch drum 401 fastened to the fixing portion 123 of the drum member 11 through the rivet 14 together with the cancel plate 307 of the clutch C3, and the planetary carrier 34 of the first planetary gear mechanism 30. (See FIG. 3), a plurality of annular clutch plates (mating plates) 403 fitted to the splines formed on the inner peripheral surface of the clutch drum 401, and the splines formed on the outer peripheral surface of the clutch hub 402 A plurality of annular clutch plates (friction plates) 404 to be combined, and a clutch piston 405 capable of pressing the clutch plates 403 and 404 are included.

  The clutch piston 405 is slidably fitted to the outer periphery of the inner cylindrical portion 121 of the inner drum 12 via a seal member, and is engaged with a spline formed on the inner periphery of the clutch drum 401. The engagement side oil chamber 406 is defined together with the inner cylinder portion 121 and the side wall portion 122. Further, a cancel plate 407 is fixed to the inner cylinder portion 121 of the inner drum 12 so as to be positioned on the clutch C1 side (left side in the drawing) with respect to the clutch piston 405. The cancel plate 407 defines a cancel oil chamber 408 for canceling centrifugal hydraulic pressure generated in the engagement side oil chamber 406 together with the clutch piston 405, and a return spring is interposed between the clutch piston 405 and the cancel plate 407. 409 is arranged. The engagement side oil chamber 406 of the clutch C4 is connected to a hydraulic control device (not shown) via an oil passage formed in the input shaft 26, the fixed shaft portion 22a, the sleeve 13, the inner cylinder portion 121 of the inner drum 12, and the like. Is done. The cancel oil chamber 408 of the clutch C4 is connected to a hydraulic control device (drain oil passage) via an oil passage formed in the input shaft 26, the fixed shaft portion 22a, the sleeve 13, the inner cylinder portion 121 of the inner drum 12, and the like. Connected.

  On the other hand, as shown in FIGS. 3 and 4, the engagement side oil chamber 306 and the cancel oil chamber 308 of the clutch C3 are viewed from the radial direction of the engagement side oil chamber 406 and the cancel oil chamber 408 on the outer peripheral side of the clutch C4. It is difficult to supply and discharge the hydraulic oil directly from the inner cylinder portion 121 of the inner drum 12 to the engagement side oil chamber 306 and the cancel oil chamber 308. For this reason, in the automatic transmission 25 according to the embodiment, the hydraulic oil can be supplied to and discharged from the engagement side oil chamber 306 and the cancel oil chamber 308 of the clutch C3 in the radial direction and radially to the side wall portion 122 of the inner drum 12. A plurality of first oil passages 124 that extend, and a plurality of second oil passages 125 that alternately extend radially and radially so as not to overlap with the plurality of first oil passages 124 when viewed from the axial direction are formed.

  Each first oil passage 124 is connected to a hydraulic control device (not shown) through an oil passage formed in the input shaft 26, the fixed shaft portion 22a, the sleeve 13, the inner cylinder portion 121 of the inner drum 12, and the like. It communicates with the engagement-side oil chamber 306 via an axial oil passage 126 formed in the side wall portion 122 so as to be positioned on the outer peripheral side of the fixing portion 123 of the drum 12. Further, each second oil passage 125 is connected to a hydraulic control device (drain oil passage) through an oil passage formed in the input shaft 26, the fixed shaft portion 22a, the sleeve 13, the inner cylinder portion 121 of the inner drum 12, and the like. At the same time, it communicates with the cancel oil chamber 308 via an axial oil passage 127 (see FIG. 4) formed in the fixed portion 123 of the inner drum 12. In this manner, the first oil passage 124 and the second oil passage 125 are formed on substantially the same plane inside the side wall portion 122 of the inner drum 12, thereby increasing the axial length of the drum member 11 and thus the clutches C3 and C4. Can be suppressed. Further, the first oil passage 124 and the second oil passage 125 are alternately formed when viewed from the axial direction, so that the hydraulic oil is supplied to the annular engagement side oil chamber 306 and the cancel oil chamber 308 substantially evenly. It becomes possible. Note that the first and second oil passages 124 and 125 have openings in the holes located on the outer peripheral side of the side wall 122 after the holes are formed from the outer peripheral side of the side wall 122 toward the radially inner side. Can be easily formed by closing with a plug.

  In the automatic transmission 25 according to the embodiment configured as described above, in addition to the input shaft 26 and the output shaft 27, in order to perform shift control more appropriately and to perform fail-safe processing more smoothly, The drum member 11 is a rotation detection target. For this reason, the rotation sensor 200 is installed in the transmission case 22 so as to face the outer peripheral surface of the outer drum 15 on the opening end surface 15o side. As shown in FIGS. 4 and 5, a concave portion 155 serving as a non-detecting portion of the rotation sensor 200 is provided on the outer peripheral surface of the outer drum 15 as an engaging surface 152 (a portion subjected to smoothing processing in the embodiment). A plurality of gaps are formed at intervals in the circumferential direction so as to be positioned closer to the opening end face 15o.

  Here, if a plurality of grooves (concave portions) extending in the axial direction from the opening end surface 15 o side are formed on the outer peripheral surface of the outer drum 15, the concave portion 155 serving as a non-detection portion of the rotation sensor 200 can be easily obtained. However, in the outer drum 15 formed by flow forming, as can be seen from FIG. 6, the residual stress after the flow forming acts radially so as to go outward from the axial center, and the stress is observed in each cross section of the outer drum 15. The deformation of the outer drum 15 is suppressed by balancing. Therefore, when a groove opened at the opening end surface 15o is formed as a non-detection portion of the rotation sensor 200 with respect to the outer drum 15, the residual stress in the groove near the opening end surface 15o of the outer drum 15 is formed as shown in FIG. Is released, and the balance of stress in the vicinity of the opening end face 15o is lost. As a result, when a groove that opens at the opening end face 15o is formed in the outer drum 15, the outer drum 15 has a portion other than the groove that extends outwardly as shown by a two-dot chain line in FIG. There is a risk of deformation.

  Based on this, as shown in FIG. 4 and FIG. 7, a plurality of concave portions 155 serving as a detected portion of the rotation sensor 200 does not open on the opening end surface 15 o on the outer peripheral surface of the outer drum 15 of the embodiment. It is formed so as to be positioned closer to the opening end surface 15o than the engaging surface 152, and the end of each recess 155 on the opening end surface 15o side is positioned closer to the engaging surface 152 than the opening end surface 15o. That is, the thickness tO of the portion of the outer drum 15 closer to the opening end face 15o than the recess 155 is thicker than the thickness tB of the portion forming the bottom of the recess 155 of the outer drum 15, and the recess 155 of the outer drum 15 is formed. It is the same as the thickness tA (see FIG. 8) of the portion (opening end portion) closer to the opening end surface 15o than the engaging surface 152 as a portion. Further, as shown in FIGS. 5 and 8, the concave portion 155 as the detected portion is constant in the circumferential direction on the outer peripheral surface on the opening end surface 15o side of the outer drum 15 so as to be located on the back side of the tooth portion 151t of the spline 151. The number of recesses 155 is smaller than the total number of teeth 151 t of the spline 151 formed on the inner periphery of the outer drum 15. Further, in the embodiment, the axial length of each recess 155 is set longer than the circumferential length (width) in consideration of the axial movement of the drum member 11 during the operation of the automatic transmission 25.

  In this way, by forming the concave portion 155 that becomes the detected portion of the rotation sensor 200 so as not to open at the opening end surface 15o of the outer drum 15, the residual stress after flow forming is released near the opening end surface 15o of the outer drum 15. Since the dent to be removed is eliminated and the stress balance in the vicinity of the opening end surface 15o is maintained, it is possible to suppress the outer drum 15 (drum member 11) from being deformed so that the opening end surface 15o side spreads (in a petal shape). it can. Therefore, in the automatic transmission 25, the rotation sensor 200 is connected to the drum member 11 while suppressing deformation of the outer drum 15 formed by flow forming so as to function as both the clutch drum of the clutch C3 and the band brake drum of the brake B1. It becomes possible to make it a rotation detection target. When the rotation sensor 200 is used without any problem even when exposed to high temperature hydraulic oil, the bottom of the recess 155 formed so as not to open at the opening end surface 15o of the outer drum 15 is removed. It may be a hole.

  As described above, the automatic transmission 25 according to the above-described embodiment has the spline 151 to which the clutch plate 303 of the clutch C3 as the first clutch is fitted on the inner peripheral side and is tightened by the brake band 10 on the outer peripheral side. The drum member 11 can be set as a rotation detection target by the rotation sensor 200 while suppressing the deformation of the outer drum 15 formed by the flow forming so as to have the cylindrical engagement surface 152. Further, by suppressing the deformation of the outer drum 15, it is possible to suppress a decrease in braking performance of the brake B1 that uses the drum member 11 as a band brake drum, and to smoothly operate the clutch C3 that uses the drum member 11 as a clutch drum. Can be made.

  Further, as in the above embodiment, if the thickness to of the portion closer to the opening end face 15o than the recess 155 of the outer drum 15 is made thicker than the thickness tB of the portion forming the bottom of the recess 155 of the outer drum 15, the outer drum 15 It becomes possible not to form a recess for releasing the residual stress after the flow forming in the vicinity of the opening end face 15o of the drum 15.

  Further, in the above-described embodiment, the plurality of concave portions 155 are formed on the outer peripheral surface of the outer drum 15 at intervals in the circumferential direction so as to be positioned on the back side of the tooth portion 151 t of the spline 151 formed on the inner periphery of the outer drum 15. The total number of the recesses 155 is smaller than the number of the tooth portions 151t of the spline 151. As described above, by not increasing the concave portions 155 serving as the detected portions of the rotation sensor 200 more than necessary, the deformation of the outer drum 15 and thus the drum member 11 can be suppressed more favorably.

  In the above-described embodiment, the drum member 11 is rotatably supported by the radial bearing 90 only at one position on the inner peripheral side, that is, the free end portion of the inner cylinder portion 121 as a support portion of the inner drum 12. Thus, the drum member 11 rotatably supported by the single radial bearing 90 is swung (tilted) with the free end portion (support portion) of the inner cylinder portion 121 supported by the radial bearing 90 as a fulcrum. In the brake B1 that uses the drum member 11 as a band brake drum, the influence of deformation of the outer drum 15 tends to appear on the braking performance and the like. Therefore, forming the concave portion 155 as the detected portion on the outer drum 15 so as not to open at the opening end surface 15o and suppressing the deformation of the outer drum 15 means that the outer drum 15 is formed by flow forming and one piece. This is extremely useful for suppressing a reduction in braking performance of the brake B1 including the drum member 11 rotatably supported by the radial bearing 90.

  Further, in the above-described embodiment, the first planetary gear mechanism 30, the clutch C4 (second clutch), and further the clutch C1 (third clutch) are arranged in the axial direction inside the drum member 11. As described above, when the first planetary gear mechanism 30, the clutch C4, and further the clutch C1 are arranged in the axial direction inside the drum member 11 in which the outer drum 15 is formed by flow forming, the axial length increases. The end of the outer drum 15 on the opening side is easily spread outward. Therefore, forming the concave portion 155 as the detected portion in the outer drum 15 so as not to open at the opening end surface 15o has the outer drum 15 formed by flow forming and various elements are disposed inside. This is extremely useful for suppressing deformation of the long drum member 11.

  In the above embodiment, the clutch C4 has a clutch drum (second clutch drum) 401 into which a plurality of clutch plates (second clutch plates) 403 are fitted, and the clutch drum 401 is an outer drum. 15 (automatic transmission 25) is fastened to the fixing portion 123 of the side wall 122 of the drum member 11, that is, the inner drum 12, via a rivet 14 as a fastening member extending in the axial direction. In addition, in the above embodiment, the cancel plate 307 of the clutch C3 is also fastened to the fixed portion 123 of the side wall portion 122 through the rivet 14 together with the clutch drum 401. In this way, when the clutch drum 401 of the clutch C4 and the cancel plate 307 of the clutch C3 are fastened to the drum member 11 by the rivet 14, the clutch drum 401 and the cancel plate 307 are fixed to the drum member 11 using a snap ring or the like. Compared to the case, the axial length required for fixing the clutch drum 401 and the like can be reduced. However, when the second clutch drum is fastened to the drum member 11 by the rivet 14 extending in the axial direction of the outer drum 15, the drum member 11, that is, the opening side of the outer drum 15 is loaded by a load for fastening the rivet 14. It becomes easy for the edge part of this to spread outward. Therefore, forming the concave portion 155 as the detected portion on the outer drum 15 so as not to open at the opening end surface 15o includes the drum member 11 having the outer drum 15 formed by flow forming and the clutch drum 401 etc. being fastened. It is extremely useful in suppressing the deformation of.

  Further, in the above-described embodiment, the drum member 11 includes the inner drum 12 that extends in the radial direction and has the side wall portion 122 to which the base end portion 15p of the outer drum 15 is welded to the outer periphery, and the clutch C4 is included in the clutch C3. A first oil passage 124 that is communicated with the engagement-side oil chamber 306 of the clutch C3 is disposed on the side wall 122 of the drum member 11 so as to at least partially overlap the clutch C3 as viewed from the radial direction on the circumferential side. A second oil passage 125 communicating with the oil chamber 308 is formed. As described above, when the first and second oil passages 124 and 125 are formed in the side wall portion 122 of the inner drum 12, the outer drum 15 and the inner drum 12 are connected due to the thickness of the material constituting the outer drum 15. The outer drum 15 is preferably fixed to the side wall portion 122 of the separate inner drum 12 as in the above-described embodiment, since it is difficult to form it integrally by flow forming. However, when the outer drum 15 formed by flow forming is fixed to the side wall portion 122 by welding, the alignment accuracy of the outer drum 15 may be slightly reduced as compared with the case where the entire drum member 11 is integrally formed. In the brake B1 using the drum member 11 as a band brake drum, the influence of deformation of the outer drum 15 tends to appear on the braking performance and the like. Accordingly, the concave portion 155 as the detected portion is formed on the outer drum 15 so as not to be opened at the opening end surface 15o, and the deformation of the outer drum 15 is suppressed by being formed by flow forming and the side wall portion of the inner drum 12 This is extremely useful for suppressing a reduction in braking performance of the brake B1 including the drum member 11 having the outer drum 15 welded and fixed to 122.

  In the above drum member 11, only the outer drum 15 is formed by flow forming. However, when it is not necessary to form an oil passage in the side wall 122, the entire drum member 11 is flowed. Needless to say, it may be formed by forming. Further, the clutch drum 401 and the cancel plate 307 may be fastened to the drum member 11 via bolts and nuts instead of the rivets 14.

  Here, the correspondence between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problems will be described. That is, in the above embodiment, the automatic transmission including the bottomed cylindrical drum member 11 that is also used as the clutch drum of the clutch C3 and the band brake drum of the brake B1, and the rotation sensor 200 that detects the rotation of the drum member 11. The machine 25 corresponds to a “transmission device”, and has a spline 151 on the inner peripheral side to which the clutch plate 403 of the clutch C3 is fitted, and a flow forming so as to have an engagement surface 152 to be tightened by the brake band 10 on the outer peripheral side. The outer drum 15 formed by the structure corresponds to a “cylindrical portion” and is formed on the outer peripheral surface of the outer drum 15 so as to be positioned on the opening end surface 15o side of the engagement surface 152 without opening at the opening end surface 15o of the outer drum 15. The concave portion 155 that is formed and serves as a detected portion of the rotation sensor 200 corresponds to a “concave portion” That.

  However, the correspondence relationship between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problem is described in the column of means for the embodiment etc. to solve the problem. The embodiment for carrying out the invention is an example for specifically explaining the embodiment, and does not limit the elements of the invention described in the column of means for solving the problem. In other words, the examples and the like are merely specific examples of the invention described in the column of means for solving the problem, and the interpretation of the invention described in the column of means for solving the problem is not limited to that column. This should be done based on the description.

  As mentioned above, although the embodiment of the present invention has been described using examples, the present invention is not limited to the above-described examples, and various modifications can be made without departing from the scope of the present invention. Needless to say.

  The present invention can be used in the transmission manufacturing industry.

  DESCRIPTION OF SYMBOLS 10 Brake band, 11 Drum member, 12 Inner drum, 13 Sleeve, 14 Rivet, 15 Outer drum, 15o Open end surface, 15p Base end part, 16 Connecting member, 20 Power transmission device, 22 Transmission case, 22a Fixed shaft part, 23 Torque converter, 23c lock-up clutch, 23o one-way clutch, 23p pump impeller, 23s stator, 23t turbine runner, 24 oil pump, 25 automatic transmission, 26 input shaft, 27 output shaft, 28 gear mechanism, 29 differential mechanism, 30 First planetary gear mechanism, 31 sun gear, 32 ring gear, 33a, 33b pinion gear, 34 planetary carrier, 35 second planetary gear mechanism, 36a first sun gear, 36b second sun gear, 37 ring gear, 38a Short pinion gear, 38b Long pinion gear, 39 Planetary carrier, 90 Radial bearing, 100 Connecting member, 100a Cylindrical part, 101, 401 Clutch drum, 102, 402 Clutch hub, 103, 104, 303, 304, 403, 404 Clutch plate, 105, 305, 405 Clutch piston, 106, 306, 406 Engagement side oil chamber, 107, 307, 407 Cancel plate, 108, 308, 408 Cancel oil chamber, 109, 309, 409 Return spring, 121 Inner cylinder, 122 Side wall portion, 123 fixing portion, 123a aligning portion, 124 first oil passage, 125 second oil passage, 126, 127 axial oil passage, 151 spline, 151t tooth portion, 152 engagement surface, 155 recess, 200 rotation sensor , 1, B2 brake, C1, C2, C3, C4 clutch, F1 the one-way clutch.

Claims (7)

  1. In a transmission including a bottomed cylindrical drum member that is also used as a clutch drum and a band brake drum, and a rotation sensor that detects rotation of the drum member,
    At least the cylindrical portion of the drum member is formed by flow forming so as to have a spline to which a clutch plate of a clutch is fitted on the inner peripheral side and an engagement surface tightened by a brake band on the outer peripheral side,
    On the outer peripheral surface of the cylindrical portion, a recess serving as a detected portion of the rotation sensor is formed so as to be positioned closer to the opening end surface than the engagement surface without opening at the opening end surface of the cylindrical portion. A transmission characterized by that.
  2. The transmission according to claim 1, wherein
    The transmission according to claim 1, wherein a thickness of a portion of the cylindrical portion closer to the opening end surface than the concave portion is thicker than a thickness of a portion of the cylindrical portion forming a bottom portion of the concave portion.
  3. The transmission according to claim 1 or 2,
    A plurality of the recesses are formed on the outer peripheral surface at intervals in the circumferential direction so as to be positioned on the back side of the teeth of the spline, and the number of the recesses is smaller than the number of teeth of the spline. Transmission device.
  4. The transmission according to any one of claims 1 to 3,
    The transmission is characterized in that the drum member is rotatably supported only at one place on the inner peripheral side.
  5. The transmission according to any one of claims 1 to 4,
    In the drum member, a planetary gear mechanism and a second clutch different from the clutch are arranged side by side in the axial direction.
  6. The transmission according to claim 5, wherein
    The second clutch has a second clutch drum to which a second clutch plate is fitted, and the second clutch drum is fastened to the drum member via a fastening member extending in the axial direction of the cylindrical portion. A transmission characterized by being made.
  7. The transmission according to claim 5 or 6,
    The drum member includes a side wall portion extending in a radial direction and having a base end portion of the cylindrical portion fixed to an outer periphery thereof,
    The second clutch is arranged on the inner peripheral side of the clutch so that at least a part thereof overlaps the clutch when viewed from the radial direction,
    An oil passage communicating with an oil chamber of the clutch is formed in the side wall portion.
JP2012018718A 2012-01-31 2012-01-31 Transmission Active JP5919850B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2012018718A JP5919850B2 (en) 2012-01-31 2012-01-31 Transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2012018718A JP5919850B2 (en) 2012-01-31 2012-01-31 Transmission

Publications (2)

Publication Number Publication Date
JP2013155849A true JP2013155849A (en) 2013-08-15
JP5919850B2 JP5919850B2 (en) 2016-05-18

Family

ID=49051241

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2012018718A Active JP5919850B2 (en) 2012-01-31 2012-01-31 Transmission

Country Status (1)

Country Link
JP (1) JP5919850B2 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015152009A1 (en) * 2014-03-31 2015-10-08 アイシン・エィ・ダブリュ株式会社 Transmission device
JP2016102561A (en) * 2014-11-28 2016-06-02 アイシン・エィ・ダブリュ株式会社 Speed change gear
US10174795B2 (en) 2014-03-31 2019-01-08 Aisin Aw Co., Ltd. Speed change device

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11342429A (en) * 1998-06-01 1999-12-14 Jatco Corp Manufacture of drum with boss and, drum with boss
JP2004169813A (en) * 2002-11-20 2004-06-17 Nsk Warner Kk Multi-plate clutch, and rotational speed detecting sensor attaching structure
JP2006083984A (en) * 2004-09-17 2006-03-30 Toyota Motor Corp Clutch device of automatic transmission
WO2008102909A1 (en) * 2007-02-23 2008-08-28 Aisin Aw Co., Ltd. Automatic transmission

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11342429A (en) * 1998-06-01 1999-12-14 Jatco Corp Manufacture of drum with boss and, drum with boss
JP2004169813A (en) * 2002-11-20 2004-06-17 Nsk Warner Kk Multi-plate clutch, and rotational speed detecting sensor attaching structure
JP2006083984A (en) * 2004-09-17 2006-03-30 Toyota Motor Corp Clutch device of automatic transmission
WO2008102909A1 (en) * 2007-02-23 2008-08-28 Aisin Aw Co., Ltd. Automatic transmission

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015152009A1 (en) * 2014-03-31 2015-10-08 アイシン・エィ・ダブリュ株式会社 Transmission device
JPWO2015152009A1 (en) * 2014-03-31 2017-04-13 アイシン・エィ・ダブリュ株式会社 Transmission
US9719579B2 (en) 2014-03-31 2017-08-01 Aisin Aw Co., Ltd. Speed change device
US10174795B2 (en) 2014-03-31 2019-01-08 Aisin Aw Co., Ltd. Speed change device
JP2016102561A (en) * 2014-11-28 2016-06-02 アイシン・エィ・ダブリュ株式会社 Speed change gear

Also Published As

Publication number Publication date
JP5919850B2 (en) 2016-05-18

Similar Documents

Publication Publication Date Title
US9303747B2 (en) Lock-up device for torque converter
US8016708B2 (en) Multi-speed gearbox
US8974339B2 (en) Vehicle power transmission device
JP4720301B2 (en) Automatic transmission clutch device
US5865289A (en) Hydraulic engagement apparatus for automatic transmissions
EP3045773B1 (en) Multi-stage transmission
EP1608891B1 (en) Hydrodynamic converter comprising a primary clutch
EP2088344B1 (en) Automatic transmission
DE19722151C2 (en) Torque converter with lock-up clutch
KR100900582B1 (en) Connection structure of automatic transmission
JP4747708B2 (en) Automatic transmission for vehicles
EP0051840B1 (en) Improved clutch drum for automatic automotive transmission
US8893867B2 (en) Wet clutch arrangement
US8955658B2 (en) Vehicle power transmission device
KR101202563B1 (en) Automatic transmission
JP4935006B2 (en) Fluid transmission device
JP4684321B2 (en) torque converter
JP4356679B2 (en) Friction engagement device
JP4798200B2 (en) Automatic transmission and axial clearance adjustment method thereof
US9022894B2 (en) Automatic transmission assembly
JP5012912B2 (en) Oil path structure of chain drive type oil pump
JP4725634B2 (en) Continuously Variable Transmission
US7442142B2 (en) Automatic transmission
US6662904B2 (en) Friction engagement element with lubrication
US20020059713A1 (en) Multi-disk clutch and method of manufacturing a core plate of a multi-disk clutch

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20140303

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20141117

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20141125

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20150119

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20150804

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20151005

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20160315

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20160328

R150 Certificate of patent or registration of utility model

Ref document number: 5919850

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150