JP2019065927A - Shaft support structure and power transmission device including the same - Google Patents

Abstract

To provide a compact shaft support structure having high durability, and to provide a power transmission device.SOLUTION: A support structure of a shaft fixed to a rotary member disposed in a case includes: a cylindrical shaft support part which is formed at the case and into which the shaft is inserted; a cylindrical extension part which extends from the rotary member so as to enclose the shaft support part of the case from the outer side; and a thrust radial bearing disposed between the shaft support part and the extension part in a radial direction. The extension part, the thrust radial bearing, the shaft support part, and the shaft axially overlap when viewed from the radial direction.SELECTED DRAWING: Figure 5

Description

  The present disclosure relates to a shaft support structure fixed to a clutch drum of a clutch and rotatably supported by a case, and a power transmission device including the same.

  2. Description of the Related Art Conventionally, there is known a power transmission device including an output shaft and a clutch for connecting the output shaft and an output element of a planetary gear to each other and releasing the connection between the output shaft and the output element (see, for example, Patent Document 1). An output shaft of the power transmission device is fixed to a clutch drum of a clutch, and a case through a thrust bearing disposed in order along an axial direction and a needle bearing (roller bearing) which is a radial bearing. It is rotatably supported by

JP, 2015-190494, A

  In order to increase the torque capacity of the power transmission device as described above, it is necessary to increase the capacity of the thrust bearing and the radial bearing in order to ensure durability. However, when the capacity of the thrust bearing or radial bearing in the power transmission device is increased, the axial length of the power transmission device is increased.

  Then, this indication makes it a main purpose to provide the support structure and power transmission device of the compact shaft which have high durability.

  The shaft supporting structure of the present disclosure is a shaft supporting portion fixed to a rotating member disposed in the case, the cylindrical shaft supporting portion being formed in the case and having the shaft inserted therethrough, and the rotating member A cylindrical extending portion extended from the outside so as to surround the shaft supporting portion of the case from the outside, and a thrust radial bearing disposed between the shaft supporting portion and the extending portion in the radial direction And the extending portion, the thrust radial bearing, the shaft support portion, and the shaft overlap in the axial direction as viewed in the radial direction.

  The support structure of the shaft is a thrust radial disposed between a shaft support formed on the case and an extension extending from the rotating member so as to surround the shaft support from the outside. Including the bearing, the extension, the thrust radial bearing, the shaft support and the shaft overlap in the radial direction as viewed in the radial direction. Thus, the capacity of the thrust radial bearing can be increased, and the axial length of the support structure can be shortened while suppressing the increase in size in the radial direction. As a result, it is possible to improve the durability while making the shaft support structure compact.

BRIEF DESCRIPTION OF THE DRAWINGS It is a schematic block diagram of the power transmission device containing the shaft support structure of this indication. It is an operation table | surface which shows the relationship between each gear stage in the transmission of the power transmission device of FIG. 1, the operating state of a clutch and a brake. FIG. 7 is a velocity diagram showing the ratio of the rotational speed of each rotary element to the input rotational speed in the transmission of the power transmission system of FIG. 1. It is an expanded sectional view showing a power transmission device of this indication. It is an expanded sectional view showing a power transmission device of this indication.

  Next, an embodiment 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 of the present disclosure. A power transmission 10 shown in the same figure is connected to a crankshaft (not shown) of an engine (internal combustion engine) (not shown) as a drive source vertically mounted at the front of a rear wheel drive vehicle and / or a rotor of an electric motor. Power (torque) from an engine or the like can be transmitted to left and right rear wheels (drive wheels) not shown. As illustrated, the power transmission device 10 shifts the power transmitted to the input shaft (input member) 20i from the transmission case (static member) 11, the start device (fluid transmission device) 12, the oil pump 17, etc. And the automatic transmission 20 etc. which are transmitted to the output shaft (output member) 20o.

  The launch device 12 has an input side having a front cover 13 connected to a crankshaft of the engine and / or a rotor of an electric motor via a drive plate or the like (not shown), and a pump shell closely fixed to the front cover 13. The pump impeller 140, the output side turbine runner 142 connected to the input shaft 20i of the automatic transmission 20, the pump impeller 140 and the turbine runner 142 are disposed inside and hydraulic oil (ATF) from the turbine runner 142 to the pump impeller 140 And a torque converter (fluid transmission device) having a one-way clutch 144 and the like for limiting the direction of rotation of the stator 143 in one direction. The launch device 12 may include a fluid coupling that does not have the stator 143.

  Furthermore, the start-up device 12 connects the front cover 13 connected to a crankshaft or the like of the engine and the input shaft 20i of the automatic transmission 20 to each other and releases the connection between them. And a damper mechanism 16 for damping vibration between the automatic transmission 20 and the input shaft 20i. 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 (a friction plate and a separator plate). However, the lockup clutch 15 may be a single plate friction type hydraulic clutch.

  The oil pump 17 has a rotor 170 connected to the pump impeller 140 of the launch device 12 via a chain 18, an external gear (drive gear) 171 having a plurality of external teeth and integrally rotating with the rotor 170, and And an internal gear (driven gear) 172 having a plurality of internal teeth that is one more than the total number of the external teeth meshing with the external teeth of the tooth gear 171 and eccentrically arranged with respect to the external gear 171. The oil pump 17 is driven by power from an engine transmitted through the chain 18 or the like, sucks hydraulic oil 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 through an input shaft 20i, a differential gear (not shown) and a drive shaft. In addition to 20o, single pinion type first and second planetary gears 21 and 22 arranged in the axial direction of the automatic transmission 20 (input shaft 20i and output shaft 20o), double pinion type planetary gear and single And a Ravigneaux type planetary gear mechanism 25 as a compound planetary gear mechanism configured by combining with a pinion type planetary gear. Furthermore, the automatic transmission 20 includes a clutch C1 (first clutch) as a first engagement element and a clutch C2 as a second engagement element for changing the power transmission path from the input shaft 20i to the output shaft 20o. Second clutch), clutch C3 (third clutch) as third engagement element, clutch C4 (fourth clutch) as fourth engagement element, brake B1 (first brake) as fifth engagement element, 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 type planetary gear mechanism 25 are connected to the Ravigneaux type planetary gear mechanism 25 and the second planetary gear 22 from the starting device 12 or the engine side (left side in FIG. 1). The first planetary gear 21, that is, a single pinion type planetary gear constituting the Ravigneaux type planetary gear mechanism 25, a double pinion type planetary gear constituting the Ravigneaux type planetary gear mechanism 25, the second planetary gear 22, the first planetary gear 21 It arrange | positions in the transmission case 11 so that it may align in order of. Thus, the Ravigneaux type planetary gear mechanism 25 is disposed on the front side of the vehicle so as to be close to the launch device 12. The first planetary gear 21 is disposed on the rear side of the vehicle so as to be close to the output shaft 20o. Furthermore, 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 20i, the output shaft 20o, and the like.

  The first planetary gear 21 includes a first sun gear 21s, which is an external gear, and a first ring gear 21r, which is an internal gear disposed concentrically with the first sun gear 21s, and a first sun gear 21s and a first ring gear 21r. And a first carrier 21c for holding the plurality of first pinion gears 21p rotatably and rotatably and rotatably. 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, for example, λ1 = 0.277.

  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. Further, 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. Furthermore, 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, and a second ring gear 22r that is an internal gear concentric with the second sun gear 22s, and a second sun gear 22s and a second ring gear 22r. And a second carrier (planetary carrier) 22c for holding the plurality of second pinion gears 22p rotatably and rotatably and rotatably. 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 set to, 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 always integral with the first sun gear 21s (and Coaxial) rotate or stop. However, the first sun gear 21s and the second sun gear 22s may be configured as separate bodies 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 rotates or stops integrally (or coaxially) with the output shaft 20o. Thus, the second carrier 22 c functions as an output element of the second planetary gear 22. Furthermore, 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 which are external gears, a third ring gear 23r which is an internal gear concentrically arranged with the third sun gear 23s, and a third sun gear 23s. A plurality of third pinion gears (short pinion gears) 23p meshing with the fourth sun gear 24s and a plurality of fourth pinion gears (long pinion gears) 24p meshing with the third ring gear 23r and a plurality of third pinion gears 23p And a third carrier 23c for holding the plurality of third pinion gears 23p and the plurality of fourth pinion gears 24p in a rotatable and rotatable manner and in a rotatable manner.

  Such Ravigneaux type planetary gear mechanism 25 is a compound planetary gear mechanism configured by combining a double pinion type planetary gear (third planetary gear) and a single pinion type 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 type planetary gear mechanism 25 constitute a double pinion type third planetary gear. Furthermore, 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 fourth planetary gear. Further, in the present embodiment, the Ravigneaux type planetary gear mechanism 25 has a gear ratio λ3 of the double pinion type third planetary gear (number of teeth of third sun gear 23s / number of teeth of third ring gear 23r), for example, λ3 =. And 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. Ru.

  Further, among the rotating elements constituting the Ravigneaux type planetary gear mechanism 25 (third and fourth planetary gears), the fourth sun gear 24s is a fixable element of the Ravigneaux type planetary gear mechanism 25 (second fixing of the automatic transmission 20 Function as possible elements). Further, as shown in FIG. 1, the third carrier 23c is always connected (fixed) to the input shaft 20i, and is connected to the first planetary gear 21 via the intermediate shaft 20m as a connecting member (second connecting member). It is always connected to the first carrier 21c. Thus, 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 type planetary gear mechanism 25. The third ring gear 23 r functions as a first output element of the Ravigneaux type planetary gear mechanism 25, and the third sun gear 23 s functions as a second output element of the Ravigneaux type planetary gear mechanism 25.

  The clutch C1 includes a first sun gear 21s of the first planetary gear 21 always connected and a second sun gear 22s of the second planetary gear 22 and a third ring gear 23r which is a first output element of the Ravigneaux type planetary gear mechanism 25. The connection is made and the connection between the two is released. The clutch C2 is configured such that the first sun gear 21s of the first planetary gear 21 and the second sun gear 22s of the second planetary gear 22 that are always connected, and the third sun gear 23s that is the second output element of the Ravigneaux type planetary gear mechanism 25 mutually The connection is made and the connection between the two is released. The clutch C3 mutually connects 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, and releases the connection between the two. The clutch C4 connects the first ring gear 21r, which is an output element of the first planetary gear 21, to the output shaft 20o, and releases the connection therebetween.

  The brake B1 fixes (connects) the fourth sun gear 24s, which is a fixable element of the Ravigneaux type planetary gear mechanism 25, to the transmission case 11 as a stationary member in a non-rotatable manner (connection) and fixes the fourth sun gear 24s to the transmission case 11. It is free to rotate freely. The brake B2 non-rotatably connects (connects) the second ring gear 22r, which is a fixable element of the second planetary gear 22, to the transmission case 11, and transmits the second ring gear 22r to the transmission case 11 as a stationary member. To be freely released.

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

  FIG. 2 shows an operation table representing the relationship between the shift speeds 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 rotational speed of the input shaft 20i in the automatic transmission FIG. 6 is a velocity diagram showing the ratio of the rotational speed of each rotary element to the input rotational speed). The automatic transmission 20 provides the forward gear and the reverse gear from the first gear to the tenth gear by setting the clutches C1 to C4 and the brakes B1 and B2 to the states shown in the operation table of FIG.

  As shown in FIG. 3, ten 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, A total of nine rotational elements are arranged in the order shown from the left in FIG. 3 at intervals corresponding to the gear ratios λ1, λ2, λ3, λ4. According to the order of arrangement on the velocity diagram, in this embodiment, the first sun gear 21s is used as a first rotating element of the automatic transmission 20, and the first carrier 21c is used as a second rotating element of the automatic transmission 20, The first ring gear 21 r is used as a third rotating element of the automatic transmission 20. Further, the second sun gear 22s is used as a fourth rotation element of the automatic transmission 20, the second carrier 22c is used as a fifth rotation element of the automatic transmission 20, and the second ring gear 22r is used as a fourth rotation element of the automatic transmission 20. . Furthermore, the fourth sun gear 24s is used as a seventh rotating element of the automatic transmission 20, the third carrier 23c is used as an eighth rotating element of the automatic transmission 20, and the third ring gear 23r is used as a ninth rotating element of the automatic transmission 20. The third sun gear 23s is used as a 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. Further, in the automatic transmission 20, at least one of the clutches C1 to C4 and the brakes B1 and B2 may be meshing engagement elements such as a dog clutch or a dog brake. For example, in the automatic transmission 20, a dog brake is adopted as the brake B2 which is engaged continuously when forming the first forward gear to the fourth forward gear and engaged when forming the reverse gear. Good. Furthermore, 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 may be, for example, a Simpson type or CR- type. It may be replaced by a compound planetary gear mechanism such as a CR type. Also, the above-described automatic transmission 20 may be modified to a transmission mounted on a front wheel drive vehicle.

  FIGS. 4 and 5 are enlarged sectional views showing the structure around the output shaft 20o (shaft) of the power transmission device 10 (automatic transmission 20) and the clutch C4.

  As shown in FIGS. 4 and 5, the clutch C4 is closer to the rear of the vehicle than the first planetary gear 21 so as to be closest to the output shaft 20o among the four clutches C1 to C4 and the two brakes B1 and B2. It arrange | positions on the right side in FIG. As shown, the clutch C4 includes a clutch hub 400, a clutch drum 410, a plurality of friction plates 401, a plurality of separator plates 402 and backing plates alternately arranged with the friction plates 401, a friction plate 401, and A piston 440 which presses the separator plate 402 for frictional engagement, a plurality of return springs (coil springs) SP4 which bias the piston 440 away from the friction plate 401 and the separator plate 402, and an annular cancel chamber defining member And 450.

  The clutch hub 400 is integrally formed with the first ring gear 21r of the first planetary gear 21 to be connected, and has a spline. The clutch drum 410 includes a parking gear 411 of the parking lock device and an annular drum member 412 in the present embodiment. The parking gear 411 has a plurality of gear teeth 411t formed on the outer peripheral portion, and the inner peripheral surface of the parking gear 411 is the outer peripheral surface of an annular flange portion 20f extending radially outward from the output shaft 20o. Fixed by welding. The drum member 412 is a cylindrical member having a spline formed on the inner peripheral surface, and is fixed to the outer peripheral portion of the parking gear by welding. Further, the drum member 412 axially extends from the parking gear 411 toward the second planetary gear 22 to surround the first planetary gear 21 (first ring gear 21 r). Further, the free end of the drum member 412 is always connected (fixed) to the second carrier 22c of the second planetary gear 22 via an annular connecting member 415 fitted to the spline.

  The plurality of friction plates 401 (each inner circumferential portion) of the clutch C 4 is fitted to the splines of the clutch hub 400. Thus, the plurality of friction plates 401 are supported by the clutch hub 400 so as to rotate integrally with the clutch hub 400 and to be movable in the axial direction. Further, the plurality of separator plates 402 (the respective outer peripheral portions) of the clutch C 4 are fitted to splines formed on the inner peripheral surface of the drum member 412 of the clutch drum 410. Thereby, the plurality of separator plates 402 are supported by the clutch drum 410 so as to rotate integrally with the clutch drum 410 and to be movable in the axial direction.

  The piston 440 has an annular pressure receiving portion 441 having an inner diameter larger than the outer diameter of the output shaft 20o, a cylindrical portion 442 axially extended from the outer peripheral portion of the pressure receiving portion 441, a friction plate 401 and a separator plate And a pressing portion 443 extended from the cylindrical portion 442 so as to press 402. The pressure receiving portion 441 of the piston 440 is fitted in a hole formed in the parking gear 411 of the clutch drum 410 so that the pressure receiving surface faces the flange portion 20f of the output shaft 20o.

  Further, the inner circumferential portion 451 of the cancel chamber defining member 450 is formed in a short cylindrical shape and is axially offset from the outer circumferential portion 452 toward the flange portion 20f of the output shaft 20o. As shown in FIG. 5, the inner circumferential portion 451 of the cancel chamber defining member 450 is fitted in the hole defined in the central portion of the pressure receiving portion 441 of the piston 440, and the outer circumferential portion 452 is a cylinder of the piston 440. It fits within the stem 442. Furthermore, in the inner circumferential portion 451 of the cancel chamber defining member 450, the tip end portion (the end portion on the left side in FIG. 5) of the output shaft 20o is fitted. The cancel chamber defining member 450 is mounted on the output shaft 20o using a snap ring 60 mounted in the ring groove of the output shaft 20o so as to abut on the end surface of the inner peripheral portion 451 opposite to the flange portion 20f. It is fixed. Thus, the piston 440 is radially supported by the output shaft 20 o via the inner circumferential portion 451 of the cancel chamber defining member 450.

  The piston 440, the inner circumferential portion 451 of the cancel chamber defining member 450, the parking gear 411 of the clutch drum 410, and the flange portion 20f (output shaft 20o) define an engagement oil chamber 460 of the clutch C4. Further, the cancel chamber defining member 450 and the piston 440 define a centrifugal hydraulic pressure cancel chamber 470 for canceling the centrifugal hydraulic pressure generated in the engagement oil chamber 460. That is, in the present embodiment, all the oil chambers of the clutch C4, that is, the engaging oil chamber 460 and the centrifugal hydraulic pressure canceling chamber 470, are clutches that rotate integrally with the output shaft 20o ( It is defined by the drum 410, the piston 440 and the cancel chamber defining member 450. As shown in FIGS. 4 and 5, in the centrifugal hydraulic pressure cancellation chamber 470, a plurality of return springs SP4 are circumferentially spaced so as to be located between the piston 440 and the cancellation chamber defining member 450. It is arranged. As return spring SP4, a single leaf spring may be used instead of a plurality of coil springs as illustrated.

  Further, as shown in FIGS. 4 and 5, the output shaft 20o fixed to the clutch drum 410 of the clutch C4 can receive a first ball bearing (thrust radial bearing) 70 capable of receiving both thrust load and radial load and It is rotatably supported by a shaft support 110 formed on the transmission case 11 via a second ball bearing 75 which receives a radial load. The shaft support portion 110 is a cylindrical portion extended from the rear end wall of the transmission case 11 to the vehicle front side (flange portion 20 f side) and the vehicle rear side. A cylindrical sleeve 80 is inserted (fitted) into the hole of the shaft support portion 110, and the output shaft 20 o is inserted into the sleeve 80. The first ball bearing 70 is a deep groove ball bearing including an inner race 71, an outer race 72, a plurality of balls 73, and a cage 74, and the radial direction of the cylindrical front end 110a formed on the shaft support 110 It is placed outside. The second ball bearing 75 is a radial ball bearing including an inner race, an outer race, a plurality of balls, and a cage, and is disposed between the rear end 110b of the shaft support portion 110 and the outer peripheral surface of the output shaft 20o. Ru.

  As shown in FIG. 5, the parking gear 411 of the clutch drum 410 has a cylindrical drum-side extension that projects in the axial direction from the inner peripheral portion of the parking gear 411 to the opposite side (vehicle rear side) to the drum member 412. The protrusion 411p is formed. The drum side extension 411 p has an inner diameter larger than the outer diameter of the front end 110 a of the shaft support 110, and surrounds the front end 110 a of the shaft support 110 at a radial interval. The inner race 71 of the first ball bearing 70 is press-fitted to the outer peripheral surface of the front end portion 110 a of the shaft support portion 110, and the outer periphery of the first ball bearing 70 is formed on the inner peripheral surface of the drum side extension 411 p. The race 72 is press-fit. Thus, the first ball bearing 70 is disposed between the front end 110 a of the shaft support 110 and the drum-side extension 411 p extended from the clutch drum 410 in the radial direction, and the drum-side extension 411 p The first ball bearing 70 and the shaft support 110 (front end 110 a) of the transmission case 11 overlap in a radial direction. In addition, the parking gear 411 is supported by the shaft support portion 110 (transmission case 11) via the first ball bearing 70.

  Further, in the shaft support portion 110, a first in-case oil passage 111 and a second in-case oil passage 112 are formed, to which hydraulic oil from a hydraulic control device (not shown) is independently supplied. A first oil hole 81 communicating with the first case internal oil passage 111 and a second oil hole 82 communicating with the second case internal oil passage 112 are axially inserted in the sleeve 80 inserted into the shaft support portion 110. It is formed at intervals in the direction. As shown in FIG. 5, the first oil hole 81 is formed in the sleeve 80 so as to overlap with the first ball bearing 70 as viewed in the radial direction.

  Further, the output shaft 20o includes a first outer annular oil passage 201, a first radial oil passage (first inner shaft oil passage) 202, an inner annular oil passage 203, a communicating oil passage 204, and a second outer side. An annular oil passage 205 and a second radial oil passage (second in-shaft oil passage) 206 are provided. The first outer annular oil passage 201 is formed on the outer peripheral surface of the output shaft 20 o so as to communicate with the first oil hole 81 of the sleeve 80. The first radial oil passage 202 is formed on the output shaft 20 o so as to overlap with the first ball bearing 70 when viewed from the radial direction, and is communicated with the first outer annular oil passage 201 and extends in the radial direction for output It opens at the inner peripheral side of the shaft 20o. The inner annular oil passage 203 is formed on the inner peripheral surface of the output shaft 20 o so as to communicate with the first radial oil passage 202, and has a diameter by a sleeve 85 disposed between the intermediate shaft 20 m and the output shaft 20 o It is closed from the inside of the direction. The communication oil passage 204 obliquely penetrates the output shaft 20o and communicates with the inner annular oil passage 203 and the engagement oil chamber 460 of the clutch C4. The second outer annular oil passage 205 is formed on the outer peripheral surface of the output shaft 20 o at an axial distance from the first outer annular oil passage 201 so as to communicate with the second oil hole 82 of the sleeve 80. The second radial oil passage 206 is formed in the output shaft 20 o at a distance from the first radial oil passage 202 in the axial direction, and communicates with the second outer annular oil passage 205 and extends in the radial direction. It opens at the inner peripheral surface of the output shaft 20o. The axial direction of the first radial oil passage 202 and the second radial oil passage 206, the front side (one side) of the first radial oil passage 202 in the axial direction, and the second radial oil passage 206 A seal ring (seal member) 90 for sealing a gap between the output shaft 20o and the sleeve 80 is disposed on the rear side (the other side) in the axial direction.

  Thereby, in the engagement oil chamber 460 of the clutch C4, the first in-case oil passage 111 of the shaft support portion 110, the first oil hole 81 of the sleeve 80, the first outer annular oil passage 201 of the output shaft 20o, the first An engagement hydraulic pressure (hydraulic fluid) to the clutch C4 adjusted by the hydraulic control device is supplied via the radial oil passage 202, the inner annular oil passage 203 and the communication oil passage 204. In the centrifugal hydraulic pressure cancel chamber 470, the second case internal oil passage 112 of the shaft support portion 110, the second oil hole 82 of the sleeve 80, the second outer annular oil passage 205 of the output shaft 20o, and the second radial oil passage The hydraulic oil (for example, drain oil for lubrication and cooling) from the hydraulic control device is supplied via 206. In the present embodiment, the hydraulic oil supplied to the second radial oil passage 206 flows from the second radial oil passage 206 into the inside of the intermediate shaft 20m via the internal space of the output shaft 20o, and the intermediate shaft The fluid flows into the centrifugal hydraulic pressure cancel chamber 470 through the oil passage formed at 20 m and the oil hole 451 h formed in the inner circumferential portion 451 of the cancel chamber defining member 450.

  As described above, in the power transmission device 10 (the automatic transmission 20), the cylindrical shaft support portion 110 formed in the transmission case 11 and the clutch drum of the clutch C4 to surround the shaft support portion 110 from the outside. Support of the output shaft 20 o (shaft) by the drum-side extension 411 p extended from 410 and the first ball bearing 70 disposed between the shaft support 110 and the drum-side extension 411 p in the radial direction Structure is composed. That is, in the power transmission device 10, the drum side extension portion 411p of the clutch drum 410 and the first ball bearing 70 overlap the shaft support portion 110 of the transmission case 11 as viewed in the radial direction. As a result, the capacity of the first ball bearing 70 can be increased, and the axial length of the support structure, that is, the power transmission device 10 can be shortened while suppressing an increase in size in the radial direction. As a result, compared with the case where one thrust bearing and one radial bearing are used instead of the first ball bearing 70, it is possible to improve the durability while achieving compactness of the power transmission device 10 (support structure). It becomes.

  Further, the first ball bearing 70 includes an inner race 71 held by the shaft support portion 110 (front end portion 110a) of the transmission case 11, and an outer race 72 held by the drum side extension portion 411p of the clutch drum 410. , And a plurality of balls 73, and a deep groove ball bearing. This makes it possible to realize a compact shaft support structure capable of well receiving both the thrust load and the radial load acting on the output shaft 20o. However, instead of the first ball bearing 70, other bearings that can receive both thrust load and radial load, such as double-row angular contact ball bearings, may be employed.

  Furthermore, in the power transmission device 10, the clutch drum 410 is fixed to the parking gear 411 so as to be fixed to the flange portion 20f of the output shaft 20o and to the parking gear 411 so as to be further away from the shaft support portion 110 than the parking gear 411. And a drum member 412. Further, the drum side extension portion 411 p is formed in the parking gear 411 so as to protrude to the opposite side to the drum member 412. As described above, by using the parking gear 411 as a component of the clutch drum 410, the power transmission device 10 can be made compact. Furthermore, since the parking gear 411 is supported by the shaft support portion 110 of the transmission case 11 via the first ball bearing 70, the parking gear 411 engaged with the parking pole (not shown) is inclined when the parking lock device is activated. It is possible to well suppress this. Thus, the durability of the power transmission device 10 can be further improved.

  Further, the clutch C4 of the power transmission device 10 is a piston 440 that defines an engagement oil chamber 460 with the clutch drum 410 and the flange portion 20f of the output shaft 20o, and a cancel that defines a centrifugal hydraulic pressure cancellation chamber 470 with the piston 440. And a chamber defining member 450. Furthermore, the inner circumferential portion 451 of the cancel chamber defining member 450 is axially offset from the outer circumferential portion 452 toward the flange portion 20 f. The cancel chamber defining member 450 is fixed to the output shaft 20o using a snap ring 60 disposed to abut on the end face of the inner circumferential portion 451 opposite to the flange portion 20f. Thereby, as shown in FIG. 5, the snap ring 60 may be disposed so as to overlap with the cancel chamber defining member 450 (portion between the inner circumferential portion 451 and the outer circumferential portion 452 in the axial direction) as viewed in the radial direction. Since it is possible, it is possible to further shorten the axial length of the power transmission device 10.

  Further, the piston 440 of the clutch C 4 presses the annular pressure receiving portion 441, the cylindrical portion 442 extended from the outer peripheral portion of the pressure receiving portion 441, and the cylindrical portion 442 so as to press the friction plate 401 and the separator plate 402. And a pressing portion 443 extended from the above. The inner circumferential portion 451 of the cancel chamber defining member 450 is fitted to the pressure receiving portion 441 of the piston 440, and the outer circumferential portion 452 is fitted within the cylindrical portion 442 of the piston 440. By thus supporting the piston 440 in the radial direction by the inner circumferential portion 451 of the cancel chamber defining member 450, the axial length of the power transmission device 10 can be further shortened.

  Further, in the power transmission device 10, since the first ball bearing 70 is disposed in the radial direction between the shaft support portion 110 of the transmission case 11 and the drum side extension portion 411p of the clutch drum 410, the first diameter The directional oil passage 202 can be formed on the output shaft 20 o so as to be located radially inward of the first ball bearing 70. Thus, it is possible to suppress an increase in the axial length of the power transmission 10 accompanying the formation of the oil passage communicating with the engagement oil chamber 460 and the centrifugal hydraulic pressure cancellation chamber 470 of the clutch C4. However, instead of the first radial oil passage 202, the second radial oil passage 206 may be formed on the output shaft 20o so as to be located radially inward of the first ball bearing 70, Both of the radial oil passages 202 and 206 may be formed on the output shaft 20 o so as to be positioned radially inward of the first ball bearing 70.

  In addition, although the support structure of the said embodiment is applied to the output shaft 20o fixed to the clutch drum 410, the application object of the support structure of the shaft of this indication is not restricted to this. That is, the shaft supported by the support structure of the present disclosure may be fixed to a rotating member other than the clutch drum 410, such as a single parking gear, a brake drum, a ring gear of a planetary gear, or a carrier.

  As described above, the shaft support structure of the present disclosure is formed on the case (11) in the support structure of the shaft (20o) fixed to the rotating member (410) disposed in the case (11). A cylindrical shaft support (110) through which the shaft (20o) is inserted, and extending from the rotating member (410) so as to surround the shaft support (110) of the case (11) from the outside A cylindrical extension (411p) and a thrust radial bearing (70) disposed radially between the shaft support (110) and the extension (411p), the extension The projecting portion (411p), the thrust radial bearing (70), the shaft support portion (110) and the shaft (20o) overlap in the axial direction as viewed from the radial direction.

The support structure of the shaft is a thrust radial disposed between a shaft support formed on the case and an extension extending from the rotating member so as to surround the shaft support from the outside. Including the bearing, the extension, the thrust radial bearing, the shaft support and the shaft overlap in the radial direction as viewed in the radial direction. Thus, the capacity of the thrust radial bearing can be increased, and the axial length of the support structure can be shortened while suppressing the increase in size in the radial direction. As a result, it is possible to improve the durability while making the shaft support structure compact.

  Further, the thrust radial bearing is held by an inner race (71) held by the shaft support portion (110) of the case (11) and the extension portion (411p) of the rotating member (410). It may be a ball bearing (70) including an outer race (72) and a plurality of balls (73). This makes it possible to realize a compact shaft support structure capable of well receiving both the thrust load and the radial load acting on the shaft.

  Furthermore, a first in-case oil passage (111) may be formed in the shaft support portion (110), and the shaft (20o) may be a sleeve (80) inserted into the shaft support portion (110). And the sleeve (80) may include a first oil hole (81) communicating with the first in-case oil passage (111), and the shaft (20o) may be inserted into the shaft (20o). A first in-shaft oil passage (202) communicating with the first oil hole (81) of the sleeve (80) and extending in the radial direction may be formed, as in the first shaft A seal member (90) for sealing a gap between the shaft (20o) and the sleeve (80) may be disposed on one side and the other side in the axial direction of the oil passage (202), and the thrust may be disposed Radial bearings (70) are two Serial viewed the radial direction in a range between the sealing member (90) in the axial direction may be arranged so as to overlap at least partially. That is, by arranging the thrust radial bearing in the radial direction between the shaft support portion of the case and the extension portion of the rotating member, at least the first in-shaft oil passage is positioned radially inside the thrust radial bearing Can be formed on the shaft. As a result, it is possible to suppress an increase in the axial length of the power transmission device accompanying the formation of the oil passage.

  Further, the shaft support portion (110) may be formed with a first in-case oil passage (111) and a second in-case oil passage (112) at an interval in the axial direction, and the sleeve (80) may include a second oil hole (82) communicating with the second in-case oil passage (112), and the shaft (20o) includes the second one of the sleeve (80). A second in-shaft oil passage (206) communicating with the oil hole (82) and extending in the radial direction may be formed, and the axial direction of the first in-shaft oil passage (202) may be formed. One side, the other side in the axial direction of the second in-shaft oil passage (206), and the axial direction of the first and second in-shaft oil passages (202, 206) in the axial direction, Clearance between shaft (20o) and sleeve (80) The seals sealing member (90) may be disposed.

  Furthermore, the rotating member may be a clutch drum (410) of a clutch (C4) connecting the shaft (20o) to another rotating element (21r), and the first in-shaft oil passage (202) May communicate with an engagement oil chamber (460) of the clutch (C4).

  Further, the clutch (C4) may include a centrifugal hydraulic pressure cancel chamber (470) for canceling a centrifugal hydraulic pressure generated in the engagement oil chamber (460), and the second in-shaft oil passage (206) ) May be in communication with the centrifugal hydraulic pressure cancellation chamber (470).

  Furthermore, the rotating member may be a clutch drum (410) of a clutch (C4) that connects the shaft (20o) to another rotating element (21r), and the clutch (C4) A piston (440) defining an engaging oil chamber (460) together with the flange portion (20f) and the flange portion (20f), and a cancellation chamber defining member (defining a centrifugal hydraulic pressure cancellation chamber (470) together with the piston (440) And the inner peripheral portion (451) of the cancellation chamber defining member (450) is directed from the outer peripheral portion (451) of the cancellation chamber defining member (450) to the flange portion (20f). And the cancel chamber defining member (450) is an end face of the inner peripheral portion (451) opposite to the flange portion (20f) side. It may be fixed to the shaft (20o) with a snap ring (60) which is arranged to abut. Thus, the snap ring can be disposed so as to overlap with the cancel chamber defining member as viewed in the radial direction, so that the axial length of the support structure of the shaft fixed to the clutch drum can be further shortened.

  Further, the piston (440) includes an annular pressure receiving portion (441), a cylindrical portion (442) extended from the outer peripheral portion of the pressure receiving portion (441), and a friction engagement plate (401, 402). And the pressing portion (443) extended from the cylindrical portion (442) to press, and the inner circumferential portion (451) of the cancellation chamber defining member (450) is the piston (440). And the outer peripheral portion (452) of the cancellation chamber defining member (450) is engaged with the cylindrical portion (442) of the piston (440). It may be done. As described above, by radially supporting the piston with the cancel chamber defining member, it is possible to further shorten the axial length of the support structure of the shaft fixed to the clutch drum.

  The power transmission device of the present disclosure is a power transmission device (10) including any one of the above-described shaft support structures and a parking lock device including a parking gear (411), wherein the shaft (20o) has a radial direction. The rotary member (410) includes the parking gear (411) fixed to the flange (20f), and the extension (411p) includes the annular flange (20f) extending outward. It is formed in the parking gear (411).

  In this power transmission device, since the parking gear is supported by the shaft support portion of the case via the thrust radial bearing, tilting of the parking gear at the time of operation of the parking lock device can be favorably suppressed. This makes it possible to further improve the durability of the power transmission device.

  In addition, the rotating member is a clutch drum (410) of a clutch (C4) that connects the shaft (20o) to another rotating element (21r), and the case (11) is connected to the parking gear (411). And a drum member (412) fixed to the parking gear (411) so as to be separated from the shaft support (110), and fitted with an outer peripheral portion of the friction engagement plate (402). As described above, by using the parking gear as a component of the clutch drum, the power transmission can be made compact.

  Furthermore, the power transmission device (10) may include a transmission (20) for shifting the power transmitted to the input member (20i) and transmitting it to the output member (20o), and the shaft may be the transmission The output member (20o) of (20) may be used.

  Also, the output member (20o) may be connected to the rear wheel of the vehicle via a differential gear.

  The invention of the present disclosure is not limited to the above embodiment, and it goes without saying that various modifications can be made within the scope of the present disclosure. Furthermore, the mode for carrying out the invention is only one specific mode of the invention described in the section of the summary of the invention, and it is not limited to the elements of the invention described in the section of the summary of the invention. Absent.

  The invention of the present disclosure can be used in the manufacturing industry of planetary gear mechanisms and the like.

  Reference Signs List 10 power transmission device, 11 transmission case, 12 launch device, 13 front cover, 140 pump impeller, 142 turbine runner, 143 stator, 144 one-way clutch, 15 lockup clutch, 16 damper mechanism, 17 oil pump, 170 rotor, 171 outside Tooth gear, 172 internal gear, 18 chain, 20 automatic transmission, 20f flange, 20i input shaft, 20m intermediate shaft, 20o output shaft, 21 first planetary gear, 21c first carrier, 21p first pinion gear, 21r first 1 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 3 ring gear, 23s third sun gear, 24p fourth pinion gear, 24s fourth sun gear, 25 Ravigneaux type planetary gear mechanism, 60 snap ring, 70 first ball bearing, 71 inner race, 72 outer race, 73 ball, 74 cage, 75 second ball bearing, 80 sleeve, 81 first oil hole, 82 second oil hole, 85 sleeve, 90 seal ring, 110 shaft support, 110a front end, 110b rear end, 111 first case oil Passage, 112 second case internal oil passage, 201 first outer annular oil passage, 202 first radial oil passage, 203 inner annular oil passage, 204 communication oil passage, 205 second outer annular oil passage, 206 second radial direction Oil path, 400 clutch hub, 401 friction plate, 402 separator plate, 410 Latch drum, 411 Parking gear, 411p drum side extension, 411t gear teeth, 412 drum member, 415 connecting member, 440 piston, 441 pressure receiving portion, 442 cylindrical portion, 443 pressing portion, 450 canceling chamber defining member, 451 Inner circumference, 451h oil hole, 452 outer circumference, 460 engagement oil chamber, 470 centrifugal oil pressure cancellation chamber, B1, B2 brake, C1, C2, C3, C4 clutch, SP4 return spring.

Claims (12)

In a supporting structure of a shaft fixed to a rotating member disposed in the case,
A cylindrical shaft support formed in the case and through which the shaft is inserted;
A cylindrical extending portion extended from the rotating member so as to surround the shaft support portion of the case from the outside;
A thrust radial bearing disposed between the shaft support portion and the extension portion in the radial direction;
Equipped with
A support structure for a shaft, wherein the extension portion, the thrust radial bearing, the shaft support portion, and the shaft overlap in an axial direction as viewed in the radial direction. In the shaft supporting structure according to claim 1,
The thrust radial bearing is a ball bearing which is a ball bearing including an inner race held by the shaft support portion of the case, an outer race held by the extension portion of the rotating member, and a plurality of balls. Construction. The shaft support structure according to claim 1 or 2
A first in-case oil passage is formed in the shaft support portion,
The shaft is inserted into a sleeve inserted into the shaft support,
The sleeve includes a first oil hole communicating with the first in-case oil passage,
The shaft is formed with a first in-shaft oil passage which communicates with the first oil hole of the sleeve and extends in the radial direction.
Seal members for sealing a gap between the shaft and the sleeve are disposed on one side and the other side in the axial direction of the first in-shaft oil passage,
The support structure for a shaft, wherein the thrust radial bearing is disposed so as to at least partially overlap in the axial direction as viewed from the radial direction in a range between two seal members. In the shaft support structure according to claim 3,
In the shaft support portion, a first in-case oil passage and a second in-case oil passage are formed at intervals in the axial direction,
The sleeve includes a second oil hole communicating with the second in-case oil passage,
A second in-shaft oil passage which is in communication with the second oil hole of the sleeve and extends in the radial direction is formed in the shaft.
The one side in the axial direction of the first in-shaft oil passage, the other side in the axial direction of the second in-shaft oil passage, and the axial direction of the first and second in-shaft oil passages A support structure for the shaft on which the seal member for sealing a gap between the shaft and the sleeve is disposed. In the shaft supporting structure according to claim 3 or 4,
The rotating member is a clutch drum of a clutch that connects the shaft to another rotating element, and the first in-shaft oil passage is a shaft supporting structure that communicates with an engaging oil chamber of the clutch. In the shaft support structure according to claim 5,
The clutch includes a centrifugal oil pressure cancellation chamber for canceling a centrifugal oil pressure generated in the engagement oil chamber, and the second in-shaft oil passage is a shaft supporting structure in communication with the centrifugal oil pressure cancellation chamber. In the shaft supporting structure according to any one of claims 1 to 6,
The rotating member is a clutch drum of a clutch that connects the shaft to another rotating element,
The clutch includes a piston defining an engagement oil chamber with the clutch drum and the flange portion, and a cancellation chamber defining member defining a centrifugal hydraulic pressure cancellation chamber with the piston.
An inner peripheral portion of the cancel chamber defining member is axially offset from an outer peripheral portion of the cancel chamber defining member toward the flange portion,
The support structure for a shaft fixed to the shaft by using a snap ring arranged to abut the end surface of the inner circumferential portion opposite to the flange portion side of the inner circumferential portion. In the shaft support structure according to claim 7,
The piston includes an annular pressure receiving portion, a cylindrical portion extending from an outer peripheral portion of the pressure receiving portion, and a pressing portion extending from the cylindrical portion to press the friction engagement plate.
The inner peripheral portion of the cancel chamber defining member is fitted to the pressure receiving portion of the piston, and the outer peripheral portion of the cancel chamber defined member is a shaft fitted to the cylindrical portion of the piston Support structure. A power transmission apparatus comprising the shaft support structure according to any one of claims 1 to 8 and a parking lock apparatus including a parking gear,
The shaft includes an annular flange portion extending radially outward,
The power transmission device, wherein the rotating member includes the parking gear fixed to the flange portion, and the extending portion is formed on the parking gear. In the power transmission device according to claim 9,
The rotating member is a clutch drum of a clutch that connects the shaft to another rotating element, is fixed to the parking gear so as to be separated from the shaft support portion of the case than the parking gear, and is frictionally engaged A power transmission device comprising a drum member into which the outer periphery of a plate is fitted. The power transmission device according to claim 9 or 10
A power transmission device, comprising: a transmission for shifting power transmitted to an input member and transmitting the power to an output member, wherein the shaft is the output member of the transmission.   The power transmission device according to claim 11, wherein the output member is connected to a rear wheel of the vehicle via a differential gear.

Images