JP2019178719A - Clutch and transmission - Google Patents

Abstract

To suppress the peeling of a friction material of a friction plate.SOLUTION: A clutch hub has a hub part having a cylindrical part which is fit with a friction plate or an internal peripheral part of a separator plate, and an annular wall part extending from one end of the cylindrical part to the radial inside. A lubricating oil-chamber defining member defining a lubricating oil chamber together with an internal peripheral face of the cylindrical part and a surface of the annular wall part is fit into the cylindrical part of the hub part, and the cylindrical part of the hub part has a plurality of oil holes which communicate with the lubricating oil chamber, and penetrate the cylindrical part in a radial direction. The lubricating oil-chamber defining member has a sleeve part fit into the cylindrical part, and a flange part extending from one end of the sleeve part to the radial inside. A plurality of protrusions abutting on the other of the annular wall part and the flange part are formed at either of the annular wall part and the flange part with intervals in a peripheral direction, a flow-in part on internal peripheral side and a flow-out part on an external peripheral side of a radial lubricating oil chamber defined by the annular wall part and the flange part out of a lubricating oil chamber are positionally deviated from each other in the peripheral direction.SELECTED DRAWING: Figure 5

Description

  The present disclosure relates to a clutch and a transmission.

  Conventionally, as this type of clutch, a clutch including a friction plate, a separator plate, a clutch hub, and a piston that presses the friction plate and the separator plate has been proposed (for example, see Patent Document 1). In this clutch, the clutch hub has a hub member having a cylindrical portion into which the inner peripheral portion of the friction plate or the separator plate is fitted and an annular wall portion extending radially inward from one end of the cylindrical portion, A lubricating oil chamber defining member that defines a lubricating oil chamber together with the inner peripheral surface of the cylindrical portion and the surface of the annular wall portion is fitted into the cylindrical portion of the hub member, and the cylindrical portion of the hub member is Each has a plurality of oil holes communicating with the lubricating oil chamber and penetrating the cylindrical portion in the radial direction. By doing so, lubricating oil and cooling hydraulic oil are satisfactorily supplied to the friction plate and the separator plate.

JP 2006-125557 A

  In the above clutch device, when the clutch hub or the like rotates at a high speed, the flow rate of the hydraulic oil supplied from the lubricating oil chamber to the friction plate and the separator plate through the plurality of oil holes becomes too high, and the friction plate There was a concern that the friction material would be easily peeled off.

  The main purpose of the clutch and the transmission of the present disclosure is to suppress separation of the friction material of the friction plate.

  The clutch and the transmission of the present disclosure have taken the following means in order to achieve the main object described above.

  The clutch of the present disclosure is a clutch including a friction plate having a friction material, a separator plate, a clutch hub, and a piston that presses the friction plate and the separator plate, and the clutch hub includes the friction plate. Or a hub portion having a tubular portion to which an inner peripheral portion of the separator plate is fitted and an annular wall portion extending radially inward from one end of the tubular portion, and in the tubular portion of the hub portion. Is fitted with a lubricating oil chamber defining member that defines a lubricating oil chamber together with the inner peripheral surface of the cylindrical portion and the surface of the annular wall portion, and the cylindrical portion of the hub portion is lubricated with the lubricating portion, respectively. The lubricating oil chamber defining member has a plurality of oil holes communicating with the oil chamber and penetrating the cylindrical portion in the radial direction, and the lubricating oil chamber defining member is fitted into the cylindrical portion and one end of the sleeve portion Or A flange portion extending radially inward, and one of the annular wall portion and the flange portion has a plurality of protrusions contacting the other of the annular wall portion and the flange portion. An inflow portion on the inner peripheral side and an outflow portion on the outer peripheral side of the radial oil chamber formed at intervals in the direction and defined by the annular wall portion and the flange portion of the lubricating oil chamber are at least one. The gist is that the portion is displaced in the circumferential direction.

  In the clutch according to the present disclosure, the clutch hub includes a cylindrical portion in which an inner peripheral portion of a friction plate having a friction material or a separator plate is fitted, and an annular wall portion extending radially inward from one end of the cylindrical portion. A hub portion having a lubricating oil chamber defining member defining a lubricating oil chamber together with the inner peripheral surface of the cylindrical portion and the surface of the annular wall portion is fitted into the cylindrical portion of the hub portion. Each of the cylindrical portions has a plurality of oil holes that communicate with the lubricating oil chamber and penetrate the cylindrical portion in the radial direction. The lubricating oil chamber defining member has a sleeve portion fitted in the cylindrical portion and a flange portion extending radially inward from one end of the sleeve portion, and one of the annular wall portion and the flange portion The plurality of protrusions that contact the other of the annular wall portion and the flange portion are formed at intervals in the circumferential direction, and the radial oil defined by the annular wall portion and the flange portion of the lubricating oil chamber At least a part of the inflow portion on the inner peripheral side of the chamber and the outflow portion on the outer peripheral side is shifted in the circumferential direction. As a result, even when the clutch hub or the like rotates at a high speed, the flow rate of the hydraulic fluid supplied from the lubricating oil chamber to the friction plate and the separator plate through the plurality of oil holes is prevented from being excessively increased. It can suppress that a friction material peels.

  A transmission according to the present disclosure includes the above-described clutch, and is a transmission that shifts power transmitted to an input member and transmits it to an output member. The transmission includes an input element, a fixable element, a first output element, and a first output element. A Ravigneaux type planetary gear mechanism having two output elements, a first planetary gear having a plurality of rotating elements, a plurality of rotating elements, and closer to the Ravigneaux type planetary gear mechanism than the first planetary gear. A second planetary gear disposed; a first brake for connecting the fixable element of the Ravigneaux type planetary gear mechanism to a stationary member so as to be non-rotatable and releasing the connection; and the Ravigneaux type planetary gear mechanism. A first clutch that connects the first output element and at least one of the rotating elements of the first and second planetary gears to each other and releases the connection between the first output element and the Ravigneaux type planetary gear mechanism. The Ravigneaux type planetary gear mechanism includes a second clutch that connects the second output element and at least one of the rotating elements of the first and second planetary gears to each other and releases the connection between them. When the fixable element is fixed to be non-rotatable by the first brake, the rotation speed of the second output element is transmitted to the input element so as to be higher than the rotation speed of the first output element. The power is accelerated and transmitted to the first and second output elements, the clutch is the second clutch, and the connection target element of the clutch is the second output element of the Ravigneaux type planetary gear mechanism. It is a summary.

  Since the transmission according to the present disclosure includes the above-described clutch, the transmission has the same effect as the above-described clutch, specifically, the effect that can suppress the friction material from being separated from the friction plate. Can do.

It is a schematic block diagram of the power transmission device 10 containing the automatic transmission 20 which is a transmission by this invention. 3 is an operation table showing the relationship between each gear position of the automatic transmission 20 and the operation states of clutches C1 to C4 and brakes B1 and B2. FIG. 6 is a velocity diagram showing a ratio of a rotational speed of each rotary element to a rotational speed (input rotational speed) of an input shaft 20i in the automatic transmission 20. FIG. 3 is an enlarged cross-sectional view of a main part showing the periphery of a clutch C2 of the automatic transmission 20. 4 is a rear view showing a hub member 210 of the clutch hub 200. FIG. It is a principal part expanded sectional view which shows the clutch C2 periphery of the automatic transmission 20B. It is a rear view showing the hub member 210C. It is a rear view showing hub member 210D.

  Next, embodiments for carrying out the invention of the present disclosure will be described with reference to the drawings.

  FIG. 1 is a schematic configuration diagram of a power transmission device 10 including an automatic transmission 20 which is a transmission according to the present invention. A power transmission device 10 shown in the figure is connected to a crankshaft of an engine (internal combustion engine) (not shown) and / or a rotor of an electric motor as a drive source mounted vertically in a front portion of a rear wheel drive vehicle. Power (torque) from an engine or the like can be transmitted to left and right rear wheels (drive wheels) (not shown). As shown in the figure, the power transmission device 10 includes a transmission case in addition to the automatic transmission 20 that shifts the power transmitted from the engine or the like to the input shaft (input member) 20i and transmits it to the output shaft (output member) 20o. (Stationary member) 11, starting device (fluid transmission device) 12, oil pump 17 and the like are included.

  The starting device 12 includes a front cover 13 connected to a crankshaft of an engine and / or a rotor of an electric motor via a drive plate or the like (not shown), and an input-side pump having a pump shell closely fixed to the front cover 13. The impeller 14p, the output-side turbine runner 14t connected to the input shaft 20i of the automatic transmission 20, the pump impeller 14p, and the turbine runner 14t are arranged inside the turbine runner 14t to rectify the flow of hydraulic oil from the turbine runner 14t to the pump impeller 14p. And a torque converter having a one-way clutch 14o that is supported by a stator shaft (not shown) and restricts the rotational direction of the stator 14s to one direction.

  Further, the starting device 12 connects the front cover 13 connected to the crankshaft of the engine and the like and the input shaft 20i of the automatic transmission 20 to each other, and releases the connection between the lockup clutch 15 and the front cover 13. And a damper mechanism 16 that attenuates vibration between the input shaft 20 i of the automatic transmission 20. In the present embodiment, the lockup clutch 15 is configured as a multi-plate friction type hydraulic clutch having a plurality of friction engagement plates (friction plates and separator plates). However, the lockup clutch 15 may be a single plate friction type hydraulic clutch. The starting device 12 may include a fluid coupling that does not include the stator 14s.

  The oil pump 17 includes a pump assembly including a pump body and a pump cover, an external gear (inner rotor) connected to the pump impeller 14p of the starting device 12 via a chain or a gear train, and an internal tooth meshing with the external gear. It is configured as a gear pump having a gear (outer rotor) or the like. The oil pump 17 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 20 is configured as a 10-speed transmission, and as shown in FIG. 1, an output shaft connected to the left and right rear wheels via an input shaft 20i, a differential gear (not shown), and a drive shaft. In addition to 20o, a single pinion type first planetary gear 21 and a second planetary gear 22 arranged in the axial direction of the automatic transmission 20 (input shaft 20i and output shaft 20o), a double pinion type planetary gear and a single And a Ravigneaux type planetary gear mechanism 25 as a compound planetary gear train configured by combining with a pinion type planetary gear. Further, the automatic transmission 20 includes a clutch C1 (first clutch) as a first engagement element and a clutch C2 (second clutch) as a second engagement element for changing the power transmission path from the input shaft 20i to the output shaft 20o. A second clutch), a clutch C3 (third clutch) as a third engagement element, a clutch C4 (fourth clutch) as a fourth engagement element, a brake B1 (first brake) as a fifth engagement element, and A brake B2 (second brake) as a sixth engagement element is included.

  In the present embodiment, the first and second planetary gears 21 and 22 and the Ravigneaux planetary gear mechanism 25 are connected to the Ravigneaux planetary gear mechanism 25 and the second planetary gear 22 from the starting device 12, that is, the engine side (left side in FIG. 1). The first planetary gear 21, that is, the single pinion planetary gear constituting the Ravigneaux planetary gear mechanism 25, the double pinion planetary gear constituting the Ravigneaux planetary gear mechanism 25, the second planetary gear 22, and the first planetary gear 21. It arrange | positions in the transmission case 11 so that it may rank in order. Thereby, the Ravigneaux type planetary gear mechanism 25 is arrange | positioned at the front part side of a vehicle so that the starting apparatus 12 may be adjoined. The first planetary gear 21 is disposed on the rear side of the vehicle so as to be close to the output shaft 20o. Further, the second planetary gear 22 is disposed between the Ravigneaux type planetary gear mechanism 25 and the first planetary gear 21 in the axial direction of the input shaft 20 i, the output shaft 20 o and the like.

  The first planetary gear 21 includes a first sun gear 21s that is an external gear, a first ring gear 21r that is an internal gear disposed concentrically with the first sun gear 21s, and a first sun gear 21s and a first ring gear 21r, respectively. And a first carrier 21c that holds the plurality of first pinion gears 21p so as to freely rotate (rotate) and revolve. In the present embodiment, the gear ratio λ1 of the first planetary gear 21 (the number of teeth of the first sun gear 21s / the number of teeth of the first ring gear 21r) is set to λ1 = 0.277, for example.

  As shown in FIG. 1, the first carrier 21c of the first planetary gear 21 is always connected (fixed) to an intermediate shaft (intermediate shaft) 20m of the automatic transmission 20 connected to the input shaft 20i. Thus, when power is transmitted from the engine to the input shaft 20i, power from the engine is constantly transmitted to the first carrier 21c via the input shaft 20i and the intermediate shaft 20m. The first carrier 21c functions as an input element of the first planetary gear 21 when the clutch C4 is engaged, and idles when the clutch C4 is released. Further, the first ring gear 21r functions as an output element of the first planetary gear 21 when the clutch C4 is engaged.

  The second planetary gear 22 includes a second sun gear 22s that is an external gear, a second ring gear 22r that is an internal gear disposed concentrically with the second sun gear 22s, and a second sun gear 22s and a second ring gear 22r, respectively. And a second carrier (planetary carrier) 22c that holds the plurality of second pinion gears 22p so that they can rotate (rotate) and revolve freely. In the present embodiment, the gear ratio λ2 of the second planetary gear 22 (the number of teeth of the second sun gear 22s / the number of teeth of the second ring gear 22r) is determined to be, for example, λ2 = 0.244.

  As shown in FIG. 1, the second sun gear 22s of the second planetary gear 22 is integrated (always connected) with the first sun gear 21s of the first planetary gear 21, and is always integrated (and coaxial) with the first sun gear 21s. ) Rotate or stop. However, the first sun gear 21s and the second sun gear 22s may be configured separately and always connected via a connecting member (first connecting member) (not shown). The second carrier 22c of the second planetary gear 22 is always connected to the output shaft 20o, and always rotates or stops integrally (and coaxially) with the output shaft 20o. As a result, the second carrier 22 c functions as an output element of the second planetary gear 22. Further, the second ring gear 22 r of the second planetary gear 22 functions as a fixable element of the second planetary gear 22.

  The Ravigneaux type planetary gear mechanism 25 includes a third sun gear 23s and a fourth sun gear 24s that are external gears, a third ring gear 23r that is an internal gear disposed concentrically with the third sun gear 23s, and a third sun gear 23s. A plurality of third pinion gears (short pinion gears) 23p that mesh with the fourth sun gear 24s and a plurality of third pinion gears 23p, and a plurality of fourth pinion gears (long pinion gears) 24p that mesh with the third ring gear 23r. The third pinion gear 23p and the plurality of fourth pinion gears 24p are rotatable (rotatable) and revolved to hold the third carrier 23c.

  Such Ravigneaux planetary gear mechanism 25 is a compound planetary gear train configured by combining a double pinion planetary gear (third planetary gear) and a single pinion planetary gear (fourth planetary gear). That is, the third sun gear 23s, the third carrier 23c, the third and fourth pinion gears 23p and 24p, and the third ring gear 23r of the Ravigneaux planetary gear mechanism 25 constitute a double pinion type third planetary gear. Further, the fourth sun gear 24s, the third carrier 23c, the fourth pinion gear 24p, and the third ring gear 23r of the Ravigneaux type planetary gear mechanism 25 constitute a single pinion type fourth planetary gear. In the present embodiment, the Ravigneaux type planetary gear mechanism 25 has a gear ratio λ3 of the double pinion type third planetary gear (the number of teeth of the third sun gear 23s / the number of teeth of the third ring gear 23r), for example, λ3 = The gear ratio λ4 of the single pinion type fourth planetary gear (the number of teeth of the fourth sun gear 24s / the number of teeth of the third ring gear 23r) is, for example, λ4 = 0.581. The

  Of the rotating elements constituting the Ravigneaux type planetary gear mechanism 25 (third and fourth planetary gears), the fourth sun gear 24s is an element that can be fixed to the Ravigneaux type planetary gear mechanism 25 (the second fixing of the automatic transmission 20). Function as a possible element). Further, as shown in FIG. 1, the third carrier 23 c is always connected (fixed) to the input shaft 20 i, and the first planetary gear 21 is connected via an intermediate shaft 20 m as a connecting member (second connecting member). Always connected to the first carrier 21c. As a result, when power is transmitted from the engine to the input shaft 20i, power from the engine is constantly transmitted to the third carrier 23c via the input shaft 20i. Therefore, the third carrier 23 c functions as an input element of the Ravigneaux planetary gear mechanism 25. The third ring gear 23r functions as a first output element of the Ravigneaux planetary gear mechanism 25, and the third sun gear 23s functions as a second output element of the Ravigneaux planetary gear mechanism 25.

  The clutch C1 mutually connects the first sun gear 21s of the first planetary gear 21 and the second sun gear 22s of the second planetary gear 22 and the third ring gear 23r, which is the first output element of the Ravigneaux type planetary gear mechanism 25, to each other. It connects and cancels both connections. The clutch C2 mutually connects the first sun gear 21s of the first planetary gear 21 and the second sun gear 22s of the second planetary gear 22 and the third sun gear 23s, which is the second output element of the Ravigneaux type planetary gear mechanism 25, to each other. It connects and cancels both connections. The clutch C3 connects and disconnects the second ring gear 22r of the second planetary gear 22 and the third ring gear 23r, which is the first output element of the Ravigneaux type planetary gear mechanism 25, to each other. The clutch C4 connects the first ring gear 21r, which is the output element of the first planetary gear 21, and the output shaft 20o to each other and releases the connection between them.

  The brake B1 fixes (connects) the fourth sun gear 24s, which can be fixed to the Ravigneaux type planetary gear mechanism 25, to the transmission case 11 as a stationary member in a non-rotatable manner, and the fourth sun gear 24s to the transmission case 11. And free to rotate. The brake B2 fixes (connects) the second ring gear 22r, which is a fixable element of the second planetary gear 22, to the transmission case 11 so as not to rotate, and also fixes the second ring gear 22r to the transmission case 11 as a stationary member. It is free to rotate.

  In the present embodiment, as the clutches C1 to C4, a hydraulic servo including a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, a centrifugal hydraulic pressure cancellation chamber, and the like. A multi-plate friction type hydraulic clutch (friction engagement element) having the above is adopted. The brakes B1 and B2 include a multi-plate friction hydraulic brake having a hydraulic servo including a piston, a plurality of friction engagement plates (friction plates and separator plates), an engagement oil chamber to which hydraulic oil is supplied, and the like. Is adopted. The clutches C1 to C4 and the brakes B1 and B2 operate when hydraulic oil is supplied and discharged by the hydraulic control device.

  FIG. 2 is an operation table showing the relationship between the gears of the automatic transmission 20 and the operating states of the clutches C1 to C4 and the brakes B1 and B2. FIG. 3 shows the rotation of the input shaft 20i in the automatic transmission 20. It is a speed diagram which shows ratio of the rotational speed of each rotation element with respect to speed (input rotational speed). The automatic transmission 20 provides the forward speed and the reverse speed from the first speed to the tenth speed by setting the clutches C1 to C4 and the brakes B1 and B2 to the states shown in the operation table of FIG.

  Further, the ten first rotating elements of the first and second planetary gears 21 and 22 and the Ravigneaux type planetary gear mechanism 25 (however, since the first sun gear 21s and the second sun gear 22s are always connected, substantially A total of nine rotating elements) are arranged in the order shown in the figure from the left side in FIG. 3 at intervals according to these gear ratios λ1, λ2, λ3, and λ4. According to such an arrangement order on the speed diagram, in the present embodiment, the first sun gear 21s is the first rotating element of the automatic transmission 20, the first carrier 21c is the second rotating element of the automatic transmission 20, The first ring gear 21r is the third rotating element of the automatic transmission 20. Further, the second sun gear 22s is the fourth rotating element of the automatic transmission 20, the second carrier 22c is the fifth rotating element of the automatic transmission 20, and the second ring gear 22r is the fourth rotating element of the automatic transmission 20. . Further, the fourth sun gear 24s is the seventh rotating element of the automatic transmission 20, the third carrier 23c is the eighth rotating element of the automatic transmission 20, and the third ring gear 23r is the ninth rotating element of the automatic transmission 20. The third sun gear 23 s is the tenth rotating element of the automatic transmission 20.

  The gear ratios λ1 to λ4 of the first and second planetary gears 21 and 22 and the third and fourth planetary gears are not limited to those described above. In the automatic transmission 20, at least one of the clutches C1 to C4 and the brakes B1 and B2 may be a meshing engagement element such as a dog clutch or a dog brake. For example, in the automatic transmission 20, even when a dog brake is employed as the brake B2 that is continuously engaged when the first forward speed is established to the fourth forward speed and is engaged when the reverse speed is formed. Good. Further, in the automatic transmission 20, at least one of the first and second planetary gears 21 and 22 may be a double pinion type planetary gear, and the Ravigneaux type planetary gear mechanism 25 is, for example, a Simpson type or a CR- It may be replaced with a compound planetary gear train such as a CR type. Further, the automatic transmission 20 described above may be modified to a transmission mounted on a front wheel drive vehicle.

  FIG. 4 is an enlarged cross-sectional view of the main part showing the periphery of the clutch C2 of the automatic transmission 20, and FIG. 5 is a rear view showing the hub member 210 of the clutch hub 200. In FIG. 5, “275a”, “275b”, “275c”, and “275d” are not components of the hub member 210 alone, but an oil reservoir formed by the hub member 210 and the cancel chamber defining member 270, A radial oil chamber, a plurality of inflow parts, and a plurality of outflow parts are shown. Hereinafter, a specific configuration around the clutch C2 of the automatic transmission 20 will be described with reference to FIGS.

  In the present embodiment, the clutch C1 is disposed between the second planetary gear 22 and the Ravigneaux planetary gear mechanism 25 so as to be close to the second planetary gear 22, and the clutch C2 is at least one member of the clutch C1. It is disposed between the second planetary gear 22 and the Ravigneaux planetary gear mechanism 25 so as to be surrounded and to be close to the Ravigneaux planetary gear mechanism 25 (third planetary gear).

  As described above, the clutches C1 and C2 use the first sun gear 21s of the first planetary gear 21 and the second sun gear 22s of the second planetary gear 22 as common connection target elements. Therefore, as shown in FIG. 4, the clutches C1 and C2 are always connected (fixed) to the first sun gear 21s and the second sun gear 22s of the second planetary gear 22, and the clutch hub of the clutch C1 and the clutch of the clutch C2 The drum member 120 that functions as a drum is shared.

  The drum member 120 includes a cylindrical portion 121 shared by the clutches C <b> 1 and C <b> 2 and an annular portion 122 that extends radially inward from the inner peripheral surface of the cylindrical portion 121. A spline 121a is formed on the outer peripheral surface of the half of the cylindrical part 121 on the second planetary gear 22 side (right side in FIG. 4), and the Ravigneaux planetary gear mechanism 25 side (in FIG. 4) of the cylindrical part 121 is formed. A spline 121b is formed on the inner peripheral surface of the left half part. Further, the inner peripheral portion of the annular portion 122 is welded to the connecting member 125, and the drum member 120 is connected to the first sun gear 21 s of the first planetary gear 21 that is a connection target element of the clutches C <b> 1 and C <b> 2 via the connecting member 125. And it is always connected (fixed) to the second sun gear 22 s of the second planetary gear 22.

  In addition to the drum member 120, the clutch C1 including the drum member 120 described above is an annular member that is fitted to the spline 121a of the cylindrical portion 121 of the drum member 120 and has a friction material attached to both surfaces. A plurality of friction plates (friction engagement plates), a plurality of separator plates (friction engagement plates) and a backing plate that are alternately arranged with the friction plates and are formed on both sides smoothly, and a friction plate A piston that presses the separator plate and frictionally engages it, a plurality of return springs (coil springs) that bias the piston away from the friction plate and the separator plate, and an annular cancel plate (cancellation chamber defining member) including. Since the clutch C1 does not form the core of the present invention, detailed description is omitted.

  In addition to the drum member 120, the clutch C2 including the drum member 120 includes first and second sun gears 21s and 22s (other rotating elements) that are always connected from the third sun gear 23s of the Ravigneaux type planetary gear mechanism 25. A clutch hub 200 serving as a power transmission member for transmitting power to a plurality of members, a plurality of friction plates (first friction engagement plates) 201 which are annular members each having a friction material 201a attached to both surfaces, and the friction plates 201 are alternately arranged. A plurality of separator plates 202 (second friction engagement plates) and a backing plate that are annular members that are provided and have both surfaces formed smoothly, and a piston 240 that presses the friction plates 201 and the separator plates 202 into friction engagement. The cancel chamber defining member (lubricating oil chamber defining member) 270 and the piston 240 A plurality of return springs for urging so as to separate from the preparative 201 and the separator plate 202 (a coil spring) and a SP2.

  As shown in FIG. 4, the clutch hub 200 includes a plurality of separator plates 202 and a hub member (hub portion) 210 into which inner peripheral portions of the backing plate are fitted, and a support member 220 that supports the piston 240. The hub member 210 is made of, for example, an aluminum alloy or the like, and includes a cylindrical portion 211 and an annular wall portion 212 that extends radially inward from one end (the left end in FIG. 4) of the cylindrical portion 211. That is, the cylindrical portion 211 and the annular wall portion 212 are integrally formed by casting an aluminum alloy or the like. The support member 220 is formed of an iron alloy or the like, and includes a cylindrical shaft portion 221 and an annular engagement oil chamber defining portion 222 that extends radially outward from one end of the shaft portion 221. That is, the shaft portion 221 and the engagement oil chamber defining portion 222 are integrally formed by forging an iron alloy or the like. As shown in FIG. 4, the support member 220 (shaft portion 221) of the clutch hub 200 is coaxially and rotatably supported by the input shaft 20i via a radial bearing.

  As shown in FIGS. 4 and 5, the cylindrical portion 211 of the hub member 210 includes a plurality of splines 211 s formed on the outer peripheral surface and a cylindrical portion 211, that is, a plurality of teeth that penetrate the tooth tips of the splines 211 s in the radial direction. Oil holes 211h. A part of the plurality of oil holes 211h located on both ends of the cylindrical portion 211 is formed to be slightly inclined with respect to the radial direction of the cylindrical portion 211 as shown in FIG.

  The annular wall portion 212 of the hub member 210 has an inner peripheral portion 213 supported by the shaft portion 221 of the support member 220 via the spacer 217. Further, the annular wall portion 212 is radially inward of the tubular portion 211 and radially outward of the inner peripheral portion 213 and opposite to the tubular portion 211 (left side in FIG. 4, that is, the Ravigneaux planetary gear mechanism 25 side). A cylindrical protruding portion 214 that protrudes from the center. A spline 214s is formed on the inner peripheral surface of the protrusion 214, and the spline 214s extends in the axial direction from the third sun gear 23s (second output element) of the Ravigneaux type planetary gear mechanism 25. It is fitted to a spline 23sb formed on the outer peripheral surface of 23sa. That is, the spline 214s of the projecting portion 214 and the spline 23sb of the third sun gear 23s (shaft portion 23sa) constitute an outer spline fitting portion SLo.

  A snap ring 216 that restricts movement of the hub member 210 and the spacer 217 in the axial direction with respect to the support member 220 is attached to the distal end of the shaft portion 221 of the support member 220. A spline 221s is formed on the outer peripheral surface of the tip portion (free end portion) of the shaft portion 221 of the support member 220, and the spline 221s is fitted to the spline 23sc formed on the inner peripheral surface of the shaft portion 23sa. Is done. That is, the spline 221s of the shaft portion 221 and the spline 23sc of the third sun gear 23s (shaft portion 23sa) constitute an inner spline fitting portion SLi.

  The outer spline fitting portion SLo that is a fitting portion between the hub member 210 and the third sun gear 23s is more than the inner spline fitting portion SLi that is a fitting portion between the shaft portion 221 (support member 220) and the third sun gear 23s. Is also located radially outward. Further, the length of the inner spline fitting portion SLi in the axial direction is determined to be shorter than the length of the outer spline fitting portion SLo in the axial direction.

  In the present embodiment, the clearance in the circumferential direction of the outer spline fitting portion SLo, that is, the clearance in the circumferential direction between the tooth surface of the spline 214s of the protruding portion 214 and the tooth surface of the spline of the shaft portion 23sa is determined to be extremely small. Yes. Thereby, the inner peripheral part of the protrusion part 214 is tightly spline-fitted to the shaft part 23sa so as to rotate integrally with the third sun gear 23s that is an element to be connected to the clutch C2. In contrast, the clearance in the circumferential direction of the inner spline fitting portion SLi, that is, the clearance in the circumferential direction between the tooth surface of the spline 221s of the shaft portion 221 and the tooth surface of the spline 23sc of the shaft portion 23sa is the outer spline fitting. It is set larger than the clearance in the circumferential direction of the part SLo. Thereby, the shaft part 221 of the support member 220 is loosely fitted to the shaft part 23sa so as not to rotate with respect to the shaft part 23sa. That is, the support member 220 having the shaft portion 221 and the engagement oil chamber defining portion 222 that are integrally formed with each other is prevented from rotating with respect to the shaft portion 23sa by the inner spline fitting portion SLi.

  A plurality of friction plates 201 (respective inner peripheral portions) of the clutch C2 are splines 121b formed on the Ravigneaux planetary gear mechanism 25 side (left side in FIG. 4) half of the cylindrical portion 121 of the drum member 120 described above. Fitted. Thus, the plurality of friction plates 201 are supported by the drum member 120 that functions as a clutch drum so as to rotate integrally with the cylindrical portion 121 and be movable in the axial direction. Further, the plurality of separator plates 202 and the backing plate (the respective outer peripheral portions) of the clutch C2 are fitted into splines 211s formed on the outer peripheral surface of the cylindrical portion 211 of the clutch hub 200. Accordingly, the plurality of separator plates 202 are supported by the clutch hub 200 so as to rotate integrally with the cylindrical portion 211 and to be movable in the axial direction.

  As shown in FIG. 4, the piston 240 of the clutch C <b> 2 includes a pressure receiving portion 241 that is supported by the shaft portion 221 of the support member 220 so as to be movable in the axial direction, and a cylinder that extends from the outer periphery of the pressure receiving portion 241 in the axial direction And a plate pressing portion 243 extending radially outward from the free end of the extending portion 242 so as to contact the separator plate 202 farthest from the Ravigneaux planetary gear mechanism 25. . The piston 240 is fitted to the shaft portion 221 so as to be movable in the axial direction so that the pressure receiving portion 241 is positioned closer to the engagement oil chamber defining portion 222 than the spline 221 s of the shaft portion 221, and the drum member 120. The cylindrical portion 121 is surrounded.

  The inner peripheral surface of the extending portion 242 of the piston 240 is in sliding contact with the outer peripheral surface of the engaging oil chamber defining portion 222, and the inner peripheral surface of the extending portion 242 and the outer peripheral surface of the engaging oil chamber defining portion 222 are in contact with each other. A seal member 223 is disposed therebetween. Thus, the engagement oil chamber 250 of the clutch C2 is defined by the pressure receiving portion 241 and the extension portion 242 of the piston 240 and the engagement oil chamber defining portion 222 of the support member 220. The engagement oil chamber 250 is supplied with the engagement hydraulic pressure (hydraulic oil) to the clutch C2 regulated by the hydraulic control device via the oil passage formed in the input shaft 20i, the shaft portion 221 and the like. The pressure receiving portion 241 receives the engagement hydraulic pressure.

  In addition, a plurality of recesses 241r are formed on the engagement oil chamber defining part 222 side of the pressure receiving part 241 of the piston 240 at intervals in the circumferential direction (in this embodiment, two at 180 ° intervals). . Furthermore, the engagement oil chamber defining portion 222 has a plurality of protrusions 222p protruding toward the pressure receiving portion 241 of the piston 240 in the circumferential direction (in this embodiment, two at intervals of 180 °). Is formed. Each protrusion 222p of the engagement oil chamber defining portion 222 is loosely fitted into the corresponding recess 241r of the pressure receiving portion 241 of the piston 240. Thus, by engaging the protrusion 222p and the recess 241r, the piston 240 is prevented from rotating with respect to the engagement oil chamber defining portion 222, that is, the support member 220, and the support member 220 (the shaft portion 221 and the shaft portion 221). It is possible to prevent rotation with respect to the third sun gear 23s (shaft portion 23sa) of the Ravigneaux type planetary gear mechanism 25 via the engagement oil chamber defining portion 222). Note that at least one recess 241r and protrusion 222p may be provided in the piston 240 and the engagement oil chamber defining part 222, and three or more may be provided. The piston 240 may be provided with at least one protrusion, and the engagement oil chamber defining part 222 may be provided with a recess that engages with the protrusion.

  A cancel chamber defining member (lubricating oil chamber defining member) 270 of the clutch C <b> 2 is fitted in the cylindrical portion 211 of the hub member 210, and is a centrifugal for canceling the centrifugal hydraulic pressure generated in the engaging oil chamber 250. A hydraulic cancel chamber 290 is defined with the piston 240. As a result, in the automatic transmission 20, the engagement oil chamber 250 and the centrifugal hydraulic pressure cancellation chamber 290 of the clutch C2 are rotated integrally with the third sun gear 23s (second output element) of the Ravigneaux type planetary gear mechanism 25. The piston 240 and the cancel chamber defining member 270 are defined inside the cylindrical portion 211 of the hub member 210. The hydraulic oil pressure canceling chamber 290 is supplied with hydraulic oil (for example, lubricating / cooling drain oil) from an oil pressure control device via an oil passage formed in the input shaft 20i, the shaft portion 221 and the like.

  As shown in FIG. 4, the cancel chamber defining member 270 has a cylindrical sleeve portion 271 fitted into the cylindrical portion 211 of the hub member 210, and a diameter from one end (left end in FIG. 4) of the sleeve portion 271. And an annular flange portion 272 extending inward in the direction and extending along the surface of the annular wall portion 212 of the hub member 210. The inner peripheral surface of the sleeve portion 271 is in sliding contact with the outer peripheral surface of the extending portion 242 of the piston 240, and a seal member 244 is disposed between the inner peripheral surface of the sleeve portion 271 and the outer peripheral surface of the extending portion 242. The Furthermore, a plurality of return springs SP2 are arranged between the flange portion 272 and the pressure receiving portion 241 of the piston 240 so as to be arranged in the circumferential direction. One end of each return spring SP2 (the right end in FIG. 4) is fitted to one of the corresponding spring holding recesses formed in the pressure receiving portion 241 of the piston 240, and the other end of each return spring SP2 is a cancel chamber. It is held by a spring seat supported by the defining member 270. Accordingly, the cancel chamber defining member 270 can be pressed against the hub member 210 by the plurality of return springs SP2 and fixed to the clutch hub 200 without using a dedicated fixing component or the like. Note that a single leaf spring may be used instead of the plurality of coil springs as the return spring SP2 of the clutch C2. A plurality of projecting portions 272c (see FIG. 4) projecting radially inward are formed on the inner peripheral portion of the flange portion 272 at intervals in the circumferential direction.

  Further, the inner peripheral surface of the cylindrical portion 211 of the hub member 210 is formed in a concave cylindrical surface shape, and protrudes in two steps radially inward from the inner peripheral surface of the free end portion of the cylindrical portion 211. At the same time, an annular protrusion 211a is formed that partially contacts the outer peripheral surface of the sleeve portion 271 of the cancel chamber defining member 270. Further, as shown in FIGS. 4 and 5, a plurality of arc-shaped protrusions 212pa that contact the flange portion 272 of the cancel chamber defining member 270 are spaced apart in the circumferential direction on the annular wall portion 212 of the hub member 210. (In this embodiment, 10 are formed at equal intervals), and a plurality of (projecting portions 212pb and 212pb which are in contact with the flange portion 272 of the cancel chamber defining member 270, radially outward from the plurality of projecting portions 212pa). The same number of arc-shaped protrusions 212pb are formed at intervals in the circumferential direction (in this embodiment, 10 at equal intervals). The inner peripheral side and outer peripheral wall portions of the plurality of protrusions 212pa and the plurality of protrusions 212pb are formed so as to extend in the circumferential direction, and the side walls (inner peripheral side) of the plurality of protrusions 212pa and the plurality of protrusions 212pb. The wall portion connecting the wall portion and the outer peripheral wall portion) is formed to extend in the radial direction. The plurality of protrusions 212pa and the plurality of protrusions 212pb are formed so as to be displaced in the circumferential direction. Specifically, each protrusion 212pb is formed so as to overlap in the radial direction between two adjacent protrusions 212pa in the circumferential direction.

  The cancel chamber defining member (lubricating oil chamber defining member) 270 is pressed against the hub member 210 by a plurality of return springs SP <b> 2, whereby the inner peripheral surface of the cylindrical portion 211 of the hub member 210 and the piston of the annular wall portion 212. A lubricating oil chamber 275 is defined together with the surface on the 240 side. The lubricating oil chamber 275 extends along the inner peripheral surface of the cylindrical portion 211 and the surface of the annular wall portion 212, and the centrifugal oil pressure canceling chamber 290 on the shaft portion 221 side of the support member 220, that is, on the inner peripheral side of the clutch hub 200. Communicate with. Specifically, a cylindrical space (oil sump 275a) is defined between the inner peripheral surface of the cylindrical portion 211 of the hub member 210 and the outer peripheral surface of the sleeve portion 271 of the cancel chamber defining member 270. Is done. In addition, an annular space (radial direction extending in the radial direction and the circumferential direction) is formed between the surface of the flange portion 272 and the surface of the annular wall portion 212 in contact with the plurality of protrusions 212pa and the plurality of protrusions 212pb. Oil chamber 275b) and a plurality of communication paths (inner side inflow portions 275c) that extend in the radial direction between two adjacent protrusions 212pa and communicate with the centrifugal hydraulic pressure cancellation chamber 290 are adjacent to each other. A plurality of communication passages (outflow portions 275d on the outer peripheral side) extending in the radial direction between the two protrusions 212pb and communicating with the oil sump portion 275a are defined. As described above, the plurality of protrusions 212pa and the plurality of protrusions 212pb are shifted in the circumferential direction (each protrusion 212pb is formed so as to overlap in the radial direction between the adjacent two protrusions 212pa in the circumferential direction. ), The inflow portions 275c and the outflow portions 275d are shifted in the circumferential direction. More specifically, each inflow portion 275c and each outflow portion 275d are shifted in the circumferential direction so as not to overlap in the radial direction. Further, the lubricating oil chamber 275 communicates with the outside of the cylindrical portion 211, that is, the friction plate 201 and the separator plate 202 side via a plurality of oil holes 211 h formed in the cylindrical portion 211.

  Next, the operation of the automatic transmission 20 will be described. In the automatic transmission 20 described above, when the clutch C2 is engaged in association with the formation of the forward first speed, the third speed, the fifth speed, and the tenth speed, the Ravigneaux planetary gear mechanism 25 The torque output from the 3 sun gear 23s (second output element) is always connected through the clutch hub 200 (hub member 210), the separator plate 202, the friction plate 201, the drum member 120, and the connecting member 125. This is transmitted to the first sun gear 21 s of the planetary gear 21 and the second sun gear 22 s of the second planetary gear 22.

  Here, in the clutch C2, the protruding portion 214 of the hub member 210 is tightly splined to the shaft portion 23sa so as to rotate integrally with the third sun gear 23s, whereas the shaft portion 221 of the support member 220 is The shaft portion 23sa is loosely spline-fitted so as not to rotate with respect to the shaft portion 23sa. That is, the clearance in the circumferential direction of the inner spline fitting portion SLi constituted by the spline 221s of the shaft portion 221 and the spline 23sc of the third sun gear 23s (shaft portion 23sa) is the same as the spline 214s of the protruding portion 214 of the hub member 210. It is larger than the outer spline fitting portion SLo formed by the spline 23sb of the third sun gear 23s (shaft portion 23sa). Therefore, in the clutch hub 200, the supporting member 220, that is, the shaft portion 221 and the engaging oil chamber defining portion 222 that are integrally formed with each other are prevented from rotating with respect to the third sun gear 23s, and the shaft portion 221 and the engaging portion are engaged. It is possible to prevent torque from being transmitted from the third sun gear 23 s to the oil chamber defining unit 222. As a result, the durability can be improved while reducing the size and weight of the support member 220 (the shaft portion 221 and the engagement oil chamber defining portion 222) and the clutch hub 200 as a whole.

  Moreover, the outer side spline fitting part SLo is located in the radial direction outer side rather than the inner side spline fitting part SLi. Therefore, the torque radius of the outer spline fitting portion SLo that is the fitting portion between the protruding portion 214 of the hub member 210 and the third sun gear 23s (shaft portion 23sa) can be increased. The increase in the axial length of the clutch C2 can be suppressed.

  In the automatic transmission 20, when the forward third speed, the fifth speed, and the tenth speed are formed, the brake B1 is engaged in addition to the clutch C2, so that the Ravigneaux planetary gear mechanism 25 is engaged. The fourth sun gear 24s (fixable element) is fixed so as not to rotate (see FIG. 2). As a result, the third carrier rotates from the input shaft 20i so that the rotational speed of the third sun gear 23s (second output element) is higher than the rotational speed of the third ring gear 23r (first output element) by the Ravigneaux planetary gear mechanism 25. The power transmitted to 23c (input element) is increased and transmitted to the third sun gear 23s and the third ring gear 23r (see FIG. 3). Thereby, during the operation of the automatic transmission 20, the third sun gear 23s (and the third ring gear 23r) of the Ravigneaux type planetary gear mechanism 25 is more than the third carrier 23c, that is, the input shaft 20i or more, except when the reverse gear is formed. It rotates at the rotation speed. Therefore, by reducing the size and weight of the clutch hub 200 of the clutch C2 and improving the durability, the third sun gear 23s that rotates at a higher speed than the input shaft 20i and the third ring gear 23r and the clutch hub that rotates integrally therewith. The inertia at the time of rotation of 200 can be reduced to improve the speed change performance of the automatic transmission 20, and the durability of the automatic transmission 20 can be ensured satisfactorily.

  In the clutch C2, a plurality of protrusions 222p projecting toward the pressure receiving part 241 of the piston 240 are formed in the engagement oil chamber defining part 222 of the support member 220, and the pressure receiving part 241 is associated with the protrusion 222p. A plurality of concave portions 241r are formed. Accordingly, the piston 240 can be prevented from rotating with respect to the hub member 210 by the support member 220 (the shaft portion 221 and the engagement oil chamber defining portion 222) while suppressing an increase in the size of the clutch C2. Therefore, the relative rotation between the piston 240 and the engagement oil chamber defining part 222 and the relative rotation between the piston 240 and the third sun gear 23s are well regulated, and the wear of the piston 240 and the engagement oil chamber defining part 222 is good. And the durability of the clutch hub 200 can be improved. Further, by forming a plurality of protrusions 222p in the engagement oil chamber defining portion 222, a decrease in the thickness of the engagement oil chamber defining portion 222 is suppressed, and the engagement oil chamber defining portion 222 Good durability can be secured. In addition, the relative rotation between the constituent members of the third sun gear 23s rotating at a higher speed than the input shaft 20i and the third ring gear 23r and the clutch hub 200 rotating integrally with the third sun gear 23r is well regulated to improve durability. The durability of the automatic transmission 20 can be further improved.

  Further, in the clutch C 2, the space defined by the cylindrical portion 211 and the annular wall portion 212 of the hub member 210 and the piston 240 is partitioned into a centrifugal hydraulic pressure cancel chamber 290 and a lubricating oil chamber 275 by the cancel chamber defining member 270. The centrifugal oil pressure cancellation chamber 290 and the lubricating oil chamber 275 communicate with each other on the shaft portion 221 side of the support member 220 of the clutch hub 200.

  Here, the cancel chamber defining member 270 includes a sleeve portion 271 fitted into the tubular portion 211 of the hub member 210 and a flange portion 272 extending radially inward from one end of the sleeve portion 271. . An annular protrusion 211a that protrudes radially inward and partially abuts on the outer peripheral surface of the sleeve portion 271 is formed on the inner peripheral surface of the free end portion of the cylindrical portion 211 of the hub member 210. A plurality of protrusions 212pa and a plurality of protrusions 212pb that are in contact with the flange portion 272 are formed on the annular wall 212 of 210 at intervals in the circumferential direction. Accordingly, the inner peripheral surface of the cylindrical portion 211 of the hub member 210, the surface of the annular wall portion 212, the wall surfaces of the plurality of protrusions 212pa, the plurality of protrusions 212pb, and the outer peripheral surface of the sleeve portion 271 of the cancel chamber defining member 270. And the surface of the flange portion 272, as a lubricating oil chamber 275, a cylindrical oil sump portion 275a, an annular (radially and circumferentially extending) radial oil chamber 275b, a centrifugal hydraulic pressure cancel chamber 290, and A plurality of inflow portions 275c communicating with the radial oil chamber 275b and a plurality of outflow portions 275d communicating with the radial oil chamber 275b and the oil reservoir 275d are formed. Therefore, a part of the hydraulic oil supplied to the centrifugal hydraulic pressure cancellation chamber 290 defined inside the cylindrical portion 211 is separated from the lubricating oil chamber 275 (a plurality of inflow portions 275c, a radial oil chamber 275b, and a plurality of outflow portions. 275d, oil sump 275a) and a plurality of oil holes 211h in the cylindrical portion 211, and the friction plate 201 and the separator plate 202 disposed around the cylindrical portion 211 are excellent as lubricating / cooling hydraulic fluid. Can be supplied. Then, lubrication / cooling hydraulic fluid is satisfactorily supplied to the friction plate 201 and the separator plate 202 of the clutch C2 having the third sun gear 23s rotating at a higher speed than the input shaft 20i and the third ring gear 23r as the elements to be connected. Thus, the durability of the automatic transmission 20 can be further improved.

  Moreover, the inflow portions 275c and the outflow portions 275d of the lubricating oil chamber 275 are displaced in the circumferential direction so as not to overlap in the radial direction. That is, each inflow portion 275c and each protrusion 212pb overlap in the radial direction. As a result, the hydraulic oil flowing from the centrifugal hydraulic pressure cancellation chamber 290 to the radial oil chamber 275b through the plurality of inflow portions 275c with the rotation of the third sun gear 23s hits the plurality of protrusions 212pb, thereby reducing the flow velocity of the hydraulic oil. Therefore, it is possible to suppress an increase in the flow velocity (radially outward speed) of the hydraulic oil supplied to the oil reservoir 275a via the plurality of outflow portions 275d. Therefore, even when the third sun gear 23s, the hub member 210, and the like rotate at a high speed as compared with the inflow portions 275c and the outflow portions 275d that are not displaced in the circumferential direction (overlapping in the radial direction), Hydraulic oil supplied to the friction plate 201 and the separator plate 202 from the centrifugal hydraulic pressure cancellation chamber 290 via the plurality of inflow portions 275c, the radial oil chamber 275b, the plurality of outflow portions 275d, the oil reservoir 275a, and the plurality of oil holes 211h. It can suppress that the flow velocity of becomes too high. As a result, it is possible to suppress the friction material 201a of the friction plate 201 from being peeled, and to improve the durability of the automatic transmission 20. Further, by increasing the number of the plurality of protrusions 212pa and the plurality of protrusions 212pb of the annular portion 210 of the hub member 210 (increasing the number of the inflow portions 275c and the outflow portions 275d), each inflow portion 275c and each outflow portion The hydraulic oil can be further dispersed in the portion 275d (the amount of oil per one of the inflow portion 275c and the outflow portion 275d can be reduced), and the friction material 201a of the friction plate 201 can be further prevented from being separated. The durability of the automatic transmission 20 can be further improved.

  Further, a plurality of return springs SP2 are arranged in the circumferential direction between the flange portion 272 of the cancel chamber defining member 270 and the pressure receiving portion 241 of the piston 240. Accordingly, the cancel chamber defining member 270 can be pressed against the hub member 210 by the plurality of return springs SP2 and fixed to the clutch hub 200 without using a dedicated fixing component or the like.

  In the automatic transmission 20 described above, in the annular wall portion 212 of the hub member 210, each protrusion 212pb overlaps with the corresponding inflow portion 275c in the radial direction, that is, each inflow portion 275c and each outflow portion. 275d was formed so as not to overlap at all in the radial direction. However, each protrusion 212pb is formed so as to partially overlap the corresponding inflow portion 275c in the radial direction, that is, each inflow portion 275c and each outflow portion 275d partially overlap in the radial direction. It is good. Also in this case, the third protrusion 212pb and the inflow portion 275c do not overlap at all in the radial direction, that is, the third in comparison with the case where the inflow portion 275c and the outflow portion 275d completely overlap in the radial direction. Even when the sun gear 23s, the hub member 210, and the like rotate at a high speed, it is possible to suppress the flow rate of the hydraulic oil supplied to the friction plate 201 and the separator plate 202 from becoming excessively high.

  In the automatic transmission 20 described above, the annular wall 212 of the hub member 210 is formed with the same number of protrusions 212pa and 212pb. That is, the same number of inflow portions 275c and outflow portions 275d are formed by the hub member 210 and the cancel chamber defining member 270. However, the number of the protrusions 212pa and the protrusions 212pb, that is, the number of the inflow portions 275c and the outflow portions 275d may be different from each other.

  In the automatic transmission 20 described above, a plurality of arc-shaped protrusions 212pa that contact the flange portion 272 of the cancel chamber defining member 270 are formed on the annular wall portion 212 of the hub member 210 at intervals in the circumferential direction. At the same time, a plurality of arc-shaped protrusions 212pb that are in contact with the flange portion 272 of the cancel chamber defining member 270 are formed on the outer side in the radial direction from the plurality of protrusions 212pa. However, as shown in FIG. 6, in the automatic transmission 20B, a plurality of protrusions are not formed on the annular wall portion 212B of the hub member 210B of the clutch hub 200B, and the flange portion 272B of the cancel chamber defining member 270B A plurality of arc-shaped protrusions 272pa that contact the annular wall portion 212B of the hub member 210B are formed at intervals in the circumferential direction, and the annular wall of the hub member 210B is radially outward from the plurality of protrusions 272pa. A plurality of arc-shaped protrusions 272pb that contact the portion 212B may be formed at intervals in the circumferential direction.

  In the automatic transmission 20 described above, in the annular wall portion 212 of the hub member 210, the inner peripheral side and the outer peripheral side wall portions of the plurality of protrusions 212pa and the plurality of protrusions 212pb are formed to extend in the circumferential direction. The side wall portions (wall portions connecting the inner peripheral wall portion and the outer peripheral wall portion) of the plurality of protrusions 212pa are formed to extend in the radial direction. However, as shown in FIG. 7, in the annular wall portion 212 </ b> C of the hub member 210 </ b> C, the side walls of the plurality of protrusions 212 pa and the plurality of protrusions 212 pb are formed to extend with an inclination with respect to the radial direction. Also good. In this case, the upstream side in the rotation direction of the hub member 210C (the direction of the thick arrow in FIG. 7) when the vehicle travels forward as the side walls of the plurality of protrusions 212pa and the plurality of protrusions 212pb move radially outward. It is preferable to be formed so as to extend. Accordingly, when the third sun gear 23s, the hub member 210, and the like rotate at a high speed, the oil reservoir 275a from the centrifugal oil pressure cancellation chamber 290 via the plurality of inflow portions 275c, the radial oil chamber 275b, and the plurality of outflow portions 275d. It is possible to more sufficiently suppress the flow velocity (radially outward speed) of the hydraulic fluid flowing through the oil reservoir 275a from the oil reservoir 275a via the plurality of oil holes 211h, and the friction plate 201 and the separator plate 202. It can suppress more fully that the flow rate of the hydraulic fluid supplied to becomes too high. As a result, the friction material 201a of the friction plate 201 can be more sufficiently prevented from being peeled, and thus the durability of the automatic transmission 20 can be further sufficiently improved.

  In the automatic transmission 20 described above, the annular wall portion 212 of the hub member 210 is formed with a plurality of arc-shaped protrusions 212pa that contact the flange portion 272 of the cancel chamber defining member 270 at intervals in the circumferential direction. In addition, a plurality of arc-shaped protrusions 212pb that are in contact with the flange portion 272 of the cancel chamber defining member 270 are formed on the outer side in the radial direction from the plurality of protrusions 212pa. . As a result, the annular wall portion 212 of the hub member 210 and the flange portion 272 of the cancel chamber defining member 270 allow the annular radial oil chamber 275b, the centrifugal oil pressure cancel chamber 290, and the radial oil in the lubricating oil chamber 275. A plurality of inflow portions 275c communicating with the chamber 275b and a plurality of outflow portions 275d communicating with the radial oil chamber 275b and the oil reservoir 275d are formed. However, as shown in FIG. 8, a plurality of arc-shaped protrusions 212pc that contact the flange portion 272 of the cancel chamber defining member 270 are formed at intervals in the circumferential direction on the annular wall portion 212D of the hub member 210D. It is good also as what is done. Here, the side walls of the plurality of protrusions 212pc are formed to extend upstream in the rotation direction of the hub member 210D (the direction of the thick arrow in FIG. 8) when the vehicle travels forward as it goes radially outward. The In this case, the lubricating oil chamber 275 is sequentially formed from the inner side in the radial direction between the two adjacent protrusions 212pc in the circumferential direction by the annular wall portion 212D of the hub member 210D and the flange portion 272 of the cancel chamber defining member 270. Inflow portion 275c, radial oil chamber 275b, and outflow portion 275d are formed. Each inflow portion 275c and each outflow portion 275d are assumed not to overlap in the radial direction. Even in such a configuration, when the third sun gear 23s, the hub member 210, and the like rotate at high speed, the centrifugal oil pressure cancellation chamber 290 passes through the plurality of inflow portions 275c, the radial oil chamber 275b, and the plurality of outflow portions 275d. It is possible to suppress the flow velocity (radially outward speed) of the hydraulic oil flowing through the oil reservoir 275a from becoming too high, and the friction plate 201 and the separator plate are connected from the oil reservoir 275a via the plurality of oil holes 211h. It can suppress more that the flow rate of the hydraulic fluid supplied to 202 becomes high too much. As a result, it is possible to suppress the friction material 201a of the friction plate 201 from being peeled, and to improve the durability of the automatic transmission 20. In place of the annular wall 212D of the hub member 210D, a plurality of arc-shaped protrusions 212pc that contact the flange 272 of the cancel chamber defining member 270 are formed at intervals in the circumferential direction. A plurality of arc-shaped projections that are in contact with the annular wall portion 212D of the hub member 210D and are similar to the plurality of projection portions 212pc are formed on the flange portion 272 of the chamber defining member 270 at intervals in the circumferential direction. It is good. Moreover, each inflow part 275c and each outflow part 275d are good also as what overlaps in a radial direction partially.

  As described above, the clutch of the present disclosure includes the friction plate (201) including the friction material (201a), the separator plate (202), the clutch hub (200, 200B), the friction plate (201), and the A clutch (C2) having a piston (240) for pressing the separator plate (202), wherein the clutch hub (200, 200B) is an inner periphery of the friction plate (201) or the separator plate (202). A hub portion (210, 210B) having a tubular portion (211) to which the portion is fitted and an annular wall portion (212, 212B, 212C, 212D) extending radially inward from one end of the tubular portion (211). , 210C, 210D) and the tubular portion (21 of the hub portion (210, 210B, 210C, 210D)) ) Includes a lubricating oil chamber defining member that defines a lubricating oil chamber (275) together with the inner peripheral surface of the cylindrical portion (211) and the surface of the annular wall portion (212, 212B, 212C, 212D). 270, 270B) are fitted, and the cylindrical portion (211) of the hub portion (210, 210B, 210C, 210D) communicates with the lubricating oil chamber (275) and the cylindrical portion (211). The lubricating oil chamber defining member (270, 270B) includes a sleeve portion (271) and a sleeve portion (271) fitted into the cylindrical portion (211). The sleeve portion (271) has a flange portion (272, 272B) extending radially inward from one end of the sleeve portion (271), and the annular wall portion (212, 212B, 212C, 212D) and the flange portion (272, 272B). One of them includes a plurality of protrusions (212pa, 212pb, 212pc, 272pa, 272pb) that are in contact with the other of the annular wall (212, 212B, 212C, 212D) and the flange (272, 272B). Are formed at intervals in the circumferential direction and are defined by the annular wall portions (212, 212B, 212C, 212D) and the flange portions (272, 272B) in the lubricating oil chamber (275). The gist is that at least a part of the inflow portion (275c) on the inner peripheral side and the outflow portion (275d) on the outer peripheral side of the chamber (275b) are shifted in the circumferential direction.

  In the clutch according to the present disclosure, the clutch hub includes a cylindrical portion in which an inner peripheral portion of a friction plate having a friction material or a separator plate is fitted, and an annular wall portion extending radially inward from one end of the cylindrical portion. A hub portion having a lubricating oil chamber defining member defining a lubricating oil chamber together with the inner peripheral surface of the cylindrical portion and the surface of the annular wall portion is fitted into the cylindrical portion of the hub portion. Each of the cylindrical portions has a plurality of oil holes that communicate with the lubricating oil chamber and penetrate the cylindrical portion in the radial direction. The lubricating oil chamber defining member has a sleeve portion fitted in the cylindrical portion and a flange portion extending radially inward from one end of the sleeve portion, and one of the annular wall portion and the flange portion The plurality of protrusions that contact the other of the annular wall portion and the flange portion are formed at intervals in the circumferential direction, and the radial oil defined by the annular wall portion and the flange portion of the lubricating oil chamber At least a part of the inflow portion on the inner peripheral side of the chamber and the outflow portion on the outer peripheral side is shifted in the circumferential direction. As a result, even when the clutch hub or the like rotates at a high speed, the flow rate of the hydraulic fluid supplied from the lubricating oil chamber to the friction plate and the separator plate through the plurality of oil holes is prevented from being excessively increased. It can suppress that a friction material peels.

  In the clutch of the present disclosure, the protrusions (212pa, 212pb, 272pa, 272pb) include a first protrusion (212pa, 272pa) formed at intervals in the circumferential direction and the first protrusion (212pa, 272pa). ) And second protrusions (212pb, 272pb) that are formed on the outer side in the radial direction and spaced apart in the circumferential direction. The inflow portions (275c) of the radial oil chamber (275b) are adjacent to each other. Between the two first protrusions (212pa, 272pa), and the outflow part (275d) of the radial oil chamber (275b) is adjacent to the two second protrusions (212pb, 272pb). ) In the circumferential direction, and the plurality of first protrusions (212pa, 272pa) and the plurality of second protrusions (212pb, 272pb) are at least Or as part are shifted in the circumferential direction. In this case, the plurality of second protrusions (212pb, 272pb) are arranged so as to overlap at least partially in the radial direction between the two adjacent first protrusions (212pa, 272pa) in the circumferential direction. It may be formed on one of the wall portion (212, 212B, 212C, 212D) and the flange portion (272, 272B). In this case, the flow rate of the hydraulic oil supplied from the lubricating oil chamber to the friction plate and the separator plate through the plurality of oil holes becomes too high due to the arrangement of the plurality of first protrusions and the plurality of second protrusions. Can be suppressed.

  In the clutch of the present disclosure, the side walls of the plurality of protrusions (212pa, 212pb, 212pc, 272pa, 272pb) may be formed to extend with an inclination with respect to the radial direction. In this case, the side wall portions of the plurality of protrusions (212pa, 212pb, 212pc, 272pa, 272pb) are formed to extend upstream in the rotational direction of the hub portion (210C, 210D) toward the radially outer side. It is good also as a thing. If it carries out like this, it can suppress that the flow velocity of the hydraulic fluid supplied to a friction plate and a separator plate from a lubricating oil chamber via a some oil hole becomes high too much with the shape of a some protrusion.

  In the clutch of the present disclosure, the inflow portion (275c) and the outflow portion (275d) may not overlap in the radial direction. By doing so, it is possible to further suppress the flow rate of the hydraulic oil supplied from the lubricating oil chamber to the friction plate and the separator plate through the plurality of oil holes from becoming too high.

  In the clutch according to the present disclosure, the clutch hub (200, 200B) includes a cylindrical shaft portion (221) that movably supports the piston (240), and an engagement oil chamber (250) to which engagement hydraulic pressure is supplied. ) And an engagement oil chamber defining portion (222) that defines the piston (240), and the lubricating oil chamber defining members (270, 270B) are disposed in the engagement oil chamber (222). A centrifugal oil pressure canceling chamber (290) for canceling the centrifugal oil pressure generated in the engine is defined together with the piston (240), and the lubricating oil chamber (275) is formed on the inner peripheral side of the clutch hub (200, 200B). The centrifugal hydraulic pressure cancellation chamber (290) may communicate with the chamber.

  In the clutch according to the present disclosure, a plurality of return springs (SP2) may be arranged in the circumferential direction between the flange portion (272, 272B) and the piston (240). In this case, the circulating oil chamber defining member can be pressed against the hub portion by a plurality of return springs and fixed to the clutch hub without using a dedicated fixing component or the like.

  The transmission according to the present disclosure is a transmission (20, 20B) that includes the above-described clutch (C2), shifts the power transmitted to the input member (20i), and transmits the power to the output member (20o). Ravigneaux type planetary gear mechanism (25) having an element (23c), a fixable element (24s), a first output element (23r) and a second output element (23s), and a first having a plurality of rotating elements A planetary gear (21) and a second planetary gear (22) having a plurality of rotating elements and disposed closer to the Ravigneaux planetary gear mechanism (25) than the first planetary gear (21); A first brake (B1) for connecting the fixable element (24s) of the Ravigneaux type planetary gear mechanism (25) to a stationary member (11) to fix the non-rotatable and releasing the connection between the two, and the Ravigneaux planetary gear mechanism (25); Type planetary gear mechanism (25 The first output element (23r) and at least one of the rotating elements of the first and second planetary gears (21, 22) are connected to each other and the first clutch (C1) for releasing the connection between them ), The second output element (23s) of the Ravigneaux type planetary gear mechanism (25), and at least one of the rotating elements of the first and second planetary gears (21, 22). And the second clutch (C2) for releasing the connection between them, the Ravigneaux planetary gear mechanism (25) has the fixable element (24s) fixed in a non-rotatable state by the first brake (B1). In this case, the power transmitted to the input element (23c) is increased so that the rotational speed of the second output element (23s) is higher than the rotational speed of the first output element (23r). 1, second output required (23r, 23s), the clutch is the second clutch (C2), and the connection target element of the clutch is the second output element (23s) of the Ravigneaux type planetary gear mechanism (25). It is a summary.

  Since the transmission according to the present disclosure includes the above-described clutch, the transmission has the same effect as the above-described clutch, specifically, the effect that can suppress the friction material from being separated from the friction plate. Can do. Further, in this transmission, the Ravigneaux type planetary gear mechanism is configured such that when the fixable element is fixed to be non-rotatable by the brake, the rotation speed of the second output element that is the connection target element of the clutch (second clutch) is the first. The power transmitted to the input element is increased so as to be higher than the rotational speed of the one output element, and is transmitted to the first and second output elements. Therefore, it is possible to improve the durability of the transmission by making it possible to satisfactorily supply lubricating and cooling oil to the friction plate and the separator plate of the clutch (second clutch).

  The transmission of the present disclosure further includes a third clutch (C3), a fourth clutch (C4), and a second brake (B2), wherein the first planetary gear (21) includes a first sun gear (21s), a first clutch The second planetary gear (22) has a second sun gear (22s), a second carrier (22c), and a second ring gear (22r), and has a carrier (21c) and a first ring gear (21r). The first sun gear (21s) of the first planetary gear (21) and the second sun gear (22s) of the second planetary gear (22) are always connected, and the first planetary gear (21) has the first sun gear (21s). One carrier (21c) is always connected to the input member (20i) and the input element (23c) of the Ravigneaux type planetary gear mechanism (25), and the second carrier (22c) of the second planetary gear (22). ) Said output The first clutch (C1) is always connected to the material (20o), and the first output gear (23r) of the Ravigneaux type planetary gear mechanism (25) is always connected to the first and second sun gears ( 21s, 22s) and the connection between them is released, and the second clutch (C2) is always connected to the second output element (23s) of the Ravigneaux type planetary gear mechanism (25). In addition, the first and second sun gears (21s, 22s) are connected to each other and disconnected from each other, and the third clutch (C3) is connected to the first output of the Ravigneaux type planetary gear mechanism (25). The element (23r) and the second ring gear (22r) of the second planetary gear (22) are connected to each other and disconnected from each other, and the fourth clutch (C4) is connected to the first planetary gear. (21) The first ring gear (21r) and the second carrier (22c) of the second planetary gear (22) are connected to each other and disconnected from each other, and the second brake (B2) The second ring gear (22r) of the planetary gear (22) may be connected to the stationary member (11) so as to be non-rotatable and the connection between both may be released.

  As mentioned above, although the form for implementing this indication was demonstrated, this indication is not limited to such embodiment at all, and can be implemented with various forms within the range which does not deviate from the gist of this indication. Of course.

  The present disclosure can be used in the manufacturing industry of clutches and transmissions.

  DESCRIPTION OF SYMBOLS 10 Power transmission device, 11 Transmission case, 12 Starting device, 13 Front cover, 14o One-way clutch, 14p Pump impeller, 14s Stator, 14t Turbine runner, 15 Lock-up clutch, 16 Damper mechanism, 17 Oil pump, 20, 20B Automatic transmission Machine, 20i input shaft, 20m intermediate shaft, 20o output shaft, 21 first planetary gear, 21c first carrier, 21p first pinion gear, 21r first ring gear, 21s first sun gear, 22 second planetary gear, 22c second carrier 22p second pinion gear, 22r second ring gear, 22s second sun gear, 23c third carrier, 23p third pinion gear, 23r third ring gear, 23s third sun gear, 23sa shaft portion, 23sb, 23sc sp IN, 24p 4th pinion gear, 24s 4th sun gear, 25 Ravigneaux type planetary gear mechanism, 120 drum member, 121 cylindrical part, 121a, 121b spline, 122 annular part, 125 connecting member, 200 clutch hub, 201 friction plate, 201a Friction material, 202 Separator plate, 210, 210B, 210C, 210D Hub member, 211 cylindrical part, 211a annular protrusion, 211h oil hole, 211s spline, 212, 212B, 212C, 212D annular wall part, 212pa, 212pb, 212pc Protruding part, 213 inner peripheral part, 214 projecting part, 214s spline, 216 snap ring, 217 spacer, 220 support member, 221 shaft part, 221s spline, 222 engaging oil chamber defining part, 222p projecting part, 23 Seal member, 240 Piston, 241 Pressure receiving portion, 241r Concavity, 242 Extension portion, 243 Plate pressing portion, 244 Seal member, 250 Engagement oil chamber, 270, 270B Cancel chamber defining member, 271 Sleeve portion, 272, 272B Flange portion, 272pa, 272pb protrusion, 272c protrusion, 275 lubricating oil chamber, 275a oil reservoir, 275b radial oil chamber, 275c inflow portion, 275d outflow portion, 290 centrifugal oil pressure cancellation chamber, B1, B2 brake, C1, C2, C3, C4 clutch, SLi inner spline fitting part, SLo outer spline fitting part, SP2 return spring.

Claims (10)

A clutch comprising a friction plate having a friction material, a separator plate, a clutch hub, and a piston that presses the friction plate and the separator plate,
The clutch hub has a hub portion having a tubular portion into which an inner peripheral portion of the friction plate or the separator plate is fitted, and an annular wall portion extending radially inward from one end of the tubular portion,
A lubricating oil chamber defining member that defines a lubricating oil chamber together with the inner peripheral surface of the cylindrical portion and the surface of the annular wall portion is fitted into the cylindrical portion of the hub portion,
The cylindrical portion of the hub portion has a plurality of oil holes that respectively communicate with the lubricating oil chamber and penetrate the cylindrical portion in the radial direction.
The lubricating oil chamber defining member has a sleeve portion fitted into the cylindrical portion and a flange portion extending radially inward from one end of the sleeve portion,
On one of the annular wall portion and the flange portion, a plurality of protrusions that contact the other of the annular wall portion and the flange portion are formed at intervals in the circumferential direction,
Among the lubricating oil chambers, at least a part of the inflow portion on the inner peripheral side and the outflow portion on the outer peripheral side of the radial oil chamber defined by the annular wall portion and the flange portion are shifted in the circumferential direction.
clutch. The clutch according to claim 1,
The protrusion includes a first protrusion formed at an interval in the circumferential direction, and a second protrusion formed at an interval in the circumferential direction radially outward from the first protrusion,
The inflow portion of the radial oil chamber is between two adjacent first protrusions in the circumferential direction,
The outflow portion of the radial oil chamber is between two adjacent second protrusions in the circumferential direction,
The plurality of first protrusions and the plurality of second protrusions are at least partially displaced in the circumferential direction.
clutch. The clutch according to claim 2,
The plurality of second protrusions are formed on one of the annular wall portion and the flange portion so as to at least partially overlap each other in the circumferential direction and in the radial direction between two adjacent first protrusions. The
clutch. The clutch according to any one of claims 1 to 3,
The side wall portions of the plurality of protrusions are formed to extend with an inclination with respect to the radial direction.
clutch. The clutch according to claim 4,
Side walls of the plurality of protrusions are formed so as to extend to the upstream side in the rotation direction of the hub portion as they go radially outward.
clutch. The clutch according to any one of claims 1 to 5,
The inflow portion and the outflow portion do not overlap in the radial direction.
clutch. The clutch according to any one of claims 1 to 6,
The clutch hub further includes a cylindrical shaft portion that movably supports the piston, and an engagement oil chamber defining portion that defines an engagement oil chamber to which engagement hydraulic pressure is supplied together with the piston. ,
The lubricating oil chamber defining member defines, together with the piston, a centrifugal oil pressure canceling chamber for canceling the centrifugal oil pressure generated in the engagement oil chamber,
The lubricating oil chamber communicates with the centrifugal oil pressure cancellation chamber on the inner peripheral side of the clutch hub;
clutch. The clutch according to any one of claims 1 to 7,
Between the flange portion and the piston, a plurality of return springs are arranged in a circumferential direction.
clutch. A transmission comprising the clutch according to any one of claims 1 to 8, wherein the transmission transmits a power transmitted to an input member to an output member.
A Ravigneaux planetary gear mechanism having an input element, a fixable element, a first output element and a second output element;
A first planetary gear having a plurality of rotating elements;
A second planetary gear having a plurality of rotating elements and disposed closer to the Ravigneaux type planetary gear mechanism than the first planetary gear;
A first brake for connecting the fixable element of the Ravigneaux type planetary gear mechanism to a stationary member to fix the non-rotatable and to release the connection between the two,
A first clutch for connecting the first output element of the Ravigneaux type planetary gear mechanism and at least one of the rotating elements of the first and second planetary gears to each other and releasing the connection therebetween;
A second clutch for connecting the second output element of the Ravigneaux type planetary gear mechanism and at least one of the rotating elements of the first and second planetary gears to each other and releasing the connection between them;
The Ravigneaux planetary gear mechanism is configured such that when the fixable element is fixed to be non-rotatable by the first brake, the rotation speed of the second output element is higher than the rotation speed of the first output element. Accelerating the power transmitted to the input element and transmitting it to the first and second output elements;
The clutch is the second clutch, and the connection target element of the clutch is the second output element of the Ravigneaux type planetary gear mechanism.
Transmission device. The transmission according to claim 9, wherein
A third clutch, a fourth clutch, and a second brake;
The first planetary gear has a first sun gear, a first carrier, and a first ring gear,
The second planetary gear has a second sun gear, a second carrier, and a second ring gear,
The first sun gear of the first planetary gear and the second sun gear of the second planetary gear are always connected,
The first carrier of the first planetary gear is always connected to the input member and the input element of the Ravigneaux planetary gear mechanism;
The second carrier of the second planetary gear is always connected to the output member;
The first clutch connects the first output element of the Ravigneaux type planetary gear mechanism and the first and second sun gears that are always connected to each other and releases the connection between them.
The second clutch connects the second output element of the Ravigneaux type planetary gear mechanism and the first and second sun gears that are always connected to each other and releases the connection between them.
The third clutch connects the first output element of the Ravigneaux planetary gear mechanism and the second ring gear of the second planetary gear to each other and releases the connection between them.
The fourth clutch connects the first ring gear of the first planetary gear and the second carrier of the second planetary gear to each other and releases the connection between them;
The second brake connects the second ring gear of the second planetary gear to the stationary member to fix the second planetary gear so as not to rotate, and releases the connection between the two,
Transmission device.