JP6333613B2 - Oil receiver - Google Patents

Description

  The present invention is supported by a planetary carrier of a planetary gear constituting a transmission, collects scattered oil, and supplies the oil to an in-shaft oil passage of a pinion shaft that is inserted into a plurality of pinion gears supported by the planetary carrier. The present invention relates to an annular oil receiver.

  Conventionally, as an oil receiver of this kind, an annular receiver disposed on the side of a planetary carrier of a planetary gear (planetary gear), and an axial oil passage formed on each of a plurality of pinion shafts supported by the planetary carrier. A plurality of protrusions that are fitted and formed with oil passages that communicate with the axial oil passages, and a plurality of protrusions that are formed so as to be recessed from the inner peripheral surface in the outer diameter direction and that communicate with the oil passages of each protrusion. What has an oil intake recessed part is known (for example, refer patent document 1). This annular receiver oil flows out from an oil supply hole formed in a cancel plate of a clutch disposed on the side of the planetary gear and scatters to the side of the planetary carrier by the action of centrifugal force. It is collected by the intake recess and supplied to the axial oil passage of each pinion shaft through the oil passage of the protruding portion. Thereby, oil (oil) as a lubricating medium is supplied to the needle bearing arranged between the pinion shaft and the pinion gear via the axial oil passage of each pinion shaft.

JP-A-2005-61450

  However, in the oil receiving recess of the conventional annular receiver, the oil (oil) that flows out from the oil outflow hole and scatters to a place away from the side of the planetary carrier (that is, inside the annular receiver) is collected. I can't. For this reason, for example, when the oil supply hole is formed at a position further away from the planetary carrier or the annular receiver, there is a possibility that oil (oil) cannot be sufficiently supplied from the annular receiver to the axial oil passage of the pinion shaft. is there.

  Therefore, the main object of the present invention is to better supply the oil scattered around the planetary carrier to the oil passage in the shaft of the pinion shaft by the oil receiver supported by the planetary carrier of the planetary gear. .

  The oil receiver according to the present invention employs the following means in order to achieve the main object.

The oil receiver according to the present invention is:
It is supported by the planetary carrier of the planetary gear constituting the transmission, and also collects the oil flowing out from the supply hole arranged closer to the planetary gear shaft than the planetary carrier and supports it by the planetary carrier. In the annular oil receiver that supplies the oil passage in the shaft of the pinion shaft inserted through the plurality of pinion gears,
An oil collecting portion that is disposed radially outside the supply hole and that is configured to collect the oil, and an oil passage that communicates with the oil collecting portion and the oil passage in the shaft, and in the shaft An annular portion including a plurality of insertion portions to be inserted into the oil passage;
An annular oil receiving portion that is formed radially outside the supply hole and radially inward of the annular portion, and receives the oil flowing out from the supply hole;
The oil receiving portion is inclined so as to be closer to the shaft center from the annular portion toward the pinion gear, and extends more radially inward than the inclined portion on the pinion gear side than the inclined portion. And a regulating wall formed as described above.

  In the oil receiver configured as described above, the oil that flows out from the supply hole arranged closer to the planetary gear shaft than the planetary carrier and scatters to the pinion gear side of the planetary gear from the annular portion of the oil receiver. At least a part of the oil is received by the regulating wall of the oil receiving portion, and is guided from the inclined portion to the oil collecting portion of the annular portion, and the oil in the shaft of the pinion shaft is passed through the oil passage of the insertion portion communicating with the oil collecting portion. Supplied to the road. As described above, in this oil receiver, the oil receiving portion formed on the radially inner side of the annular portion better receives the oil scattered in the portion separated from the oil collecting portion of the annular portion, and the inclined portion. It is possible to smoothly lead to the oil collecting part of the annular part. Therefore, according to this oil receiver, the oil scattered around the planetary carrier can be better supplied to the oil passage in the shaft of the pinion shaft.

It is a schematic block diagram of the power transmission device containing the oil receiver by this invention. 2 is an operation table showing a relationship between each shift stage of the automatic transmission included in the power transmission device of FIG. 1 and operation states of clutches and brakes. It is a fragmentary sectional view which shows the principal part of the automatic transmission contained in the power transmission device of FIG.

  Next, the form for implementing this invention is demonstrated, referring drawings.

  FIG. 1 is a schematic configuration diagram of a power transmission device 20 including an oil receiver 60 according to the present invention. A power transmission device 20 shown in the figure is connected to a crankshaft of an engine (not shown) mounted on a front wheel drive vehicle and can transmit power from the engine to left and right drive wheels (front wheels) (not shown). As shown in the figure, the power transmission device 20 includes a transmission case 22, a starting device (fluid transmission device) 23 housed in the transmission case 22, an oil pump 24, an automatic transmission 25, and a gear mechanism (gear train). 28, a differential gear (differential mechanism) 29 and the like.

  The starting device 23 includes an input-side pump impeller 23p connected to an engine crankshaft, an output-side turbine runner 23t connected to an input shaft (input member) 26 of the automatic transmission 25, a pump impeller 23p, and a turbine runner. A stator 23s that is disposed inside 23t and rectifies the flow of hydraulic oil from the turbine runner 23t to the pump impeller 23p, a one-way clutch 23o that restricts the rotation direction of the stator 23s in one direction, a lock-up clutch 23c, a damper mechanism 23d, and the like Is configured as a torque converter. However, the starting device 23 may be configured as a fluid coupling that does not include the stator 23s.

  The oil pump 24 is a gear pump having a pump assembly including a pump body and a pump cover, an external gear connected to the pump impeller 23p of the starting device 23 via a hub, an internal gear that meshes with the external gear, and the like. It is configured. The oil pump 24 is driven by power from the engine and sucks hydraulic oil (ATF) stored in an oil pan (not shown) to generate a hydraulic pressure required by the starting device 23 and the automatic transmission 25 (not shown). Pump to control unit.

  The automatic transmission 25 is configured as an 8-speed transmission, and as shown in FIG. 1, in addition to the input shaft 26, a double pinion type first planetary gear mechanism 30 and a Ravigneaux type second planetary gear. The gear mechanism 40 includes four clutches C1, C2, C3 and C4 for changing the power transmission path from the input side to the output side, two brakes B1 and B2, and a one-way clutch F1.

  The first planetary gear mechanism 30 of the automatic transmission 25 includes a sun gear 31 that is an external gear, a ring gear 32 that is an internal gear disposed concentrically with the sun gear 31, and a plurality of first gears that mesh with the sun gear 31. The first pinion gears 33a and the second pinion gears 33b that mesh with the first pinion gears 33a and the corresponding first pinion gears 33a and the ring gears 32 and that are arranged radially outside the first pinion gears 33a, and the first pinion gears 33a and second gears that mesh with each other. It has a planetary carrier 34 that holds a set of pinion gears 33b so as to be rotatable (rotatable) and revolved. As illustrated, the sun gear 31 of the first planetary gear mechanism 30 is fixed to the transmission case 22, and the planetary carrier 34 of the first planetary gear mechanism 30 is coupled to the input shaft 26 so as to be integrally rotatable. The first planetary gear mechanism 30 is configured as a so-called reduction gear, and decelerates the power transmitted to the planetary carrier 34 as an input element and outputs it from a ring gear 32 as an output element.

  The second planetary gear mechanism 40 of the automatic transmission 25 is an internal gear disposed concentrically with the first sun gear 41a and the second sun gear 41b, which are external gears, and the first and second sun gears 41a and 41b. Ring gear 42, a plurality of short pinion gears 43a meshing with first sun gear 41a, a plurality of long pinion gears 43b meshing with second sun gear 41b and a plurality of short pinion gears 43a and meshing with ring gear 42, a plurality of short pinion gears 43a and It has a planetary carrier 44 that holds a plurality of long pinion gears 43b so as to be rotatable (rotatable) and revolved. The ring gear 42 of the second planetary gear mechanism 40 functions as an output member of the automatic transmission 25, and the power transmitted from the input shaft 26 to the ring gear 42 is transmitted to the left and right drive wheels via the gear mechanism 28 and the differential gear 29. Communicated. The planetary carrier 44 is supported by the transmission case 22 via the one-way clutch F1, and the rotation direction of the planetary carrier 44 is limited to one direction by the one-way clutch F1.

  The clutch C1 has a hydraulic servo including a piston, a plurality of friction plates, a counter plate, an oil chamber to which hydraulic oil is supplied, and the like. The ring gear 32 of the first planetary gear mechanism 30 and the second planetary gear mechanism 40 This is a multi-plate friction type hydraulic clutch (friction engagement element) capable of fastening the first sun gear 41a and releasing the fastening of both. The clutch C2 has a hydraulic servo composed of a piston, a plurality of friction plates and mating plates, an oil chamber supplied with hydraulic oil, and the like, and fastens the input shaft 26 and the planetary carrier 44 of the second planetary gear mechanism 40. In addition, this is a multi-plate friction type hydraulic clutch capable of releasing the fastening of both. The clutch C3 has a hydraulic servo composed of a piston, a plurality of friction plates and mating plates, an oil chamber to which hydraulic oil is supplied, and the like. The ring gear 32 of the first planetary gear mechanism 30 and the second planetary gear mechanism 40 This is a multi-plate friction hydraulic clutch capable of fastening the second sun gear 41b and releasing the fastening of both. The clutch C4 has a hydraulic servo composed of a piston, a plurality of friction plates and a counter plate, an oil chamber to which hydraulic oil is supplied, and the like. The planetary carrier 34 and the second planetary gear mechanism 40 of the first planetary gear mechanism 30 are provided. This is a multi-plate friction type hydraulic clutch capable of fastening the second sun gear 41b and releasing the fastening of both.

  The brake B1 is configured as a band brake including a hydraulic servo or a multi-plate friction brake, and fixes the second sun gear 41b of the second planetary gear mechanism 40 to the transmission case 22 in a non-rotatable manner and the transmission of the second sun gear 41b. This is a hydraulic brake (friction engagement element) that can be released from being fixed to the case 22. The brake B2 is configured as a band brake including a hydraulic servo or a multi-plate friction brake, and fixes the planetary carrier 44 of the second planetary gear mechanism 40 to the transmission case 22 so as not to rotate, and the transmission case 22 of the planetary carrier 44. This is a hydraulic brake that can be released from the fixed state. The one-way clutch F1 includes, for example, an inner race, an outer race, and a plurality of sprags. When the outer race rotates in one direction with respect to the inner race, the one-way clutch F1 transmits torque via the sprag and Thus, when the outer race rotates in the other direction, both are rotated relative to each other. However, the one-way clutch F1 may have a configuration other than a sprag type such as a roller type.

  These clutches C1 to C4 and brakes B1 and B2 operate by receiving and discharging hydraulic oil from the hydraulic control device. FIG. 2 shows an operation table showing the relationship between the respective speeds of the automatic transmission 25 and the operating states of the clutches C1 to C4, the brakes B1 and B2, and the one-way clutch F1. The automatic transmission 25 provides the forward 1st to 8th gears and the reverse 1st and 2nd gears by setting the clutches C1 to C4 and the brakes B1 and B2 to the states shown in the operation table of FIG. . Note that at least one of the clutches C1 to C3 and the brakes B1 and B2 except the clutch C4 may be a meshing engagement element such as a dog clutch.

  FIG. 3 is a partial cross-sectional view showing a main part of the automatic transmission 25. The figure shows a configuration around the first planetary gear mechanism 30 included in the automatic transmission 25. As shown in the figure, a first pinion shaft 35 is inserted into each first pinion gear 33a of the first planetary gear mechanism 30 via a needle bearing 37, and each second pinion gear 33b is inserted through a needle bearing 38 into the first pinion gear 33a. A two-pinion shaft 36 is inserted. The plurality of first pinion shafts 35 and the plurality of second pinion shafts 36 are held by the planetary carrier 34 so that the first pinion gears 33a and the second pinion gears 33b are alternately arranged in the circumferential direction.

  As shown in FIG. 3, the planetary carrier 34 of the first planetary gear mechanism 30 includes a substantially cylindrical carrier body 341 and an annular carrier cover 342 fixed to the carrier body 341. The carrier main body 341 of the planetary carrier 34 includes an outer cylinder portion 341a extending in the axial direction of the first planetary gear mechanism 30 (the axial direction of the input shaft 26 of the automatic transmission 25), and the clutch C4 side of the outer cylinder portion 341a (see FIG. 3 and an annular bottom portion 341b extending inward in the radial direction of the first planetary gear mechanism 30 (the radial direction of the input shaft 26 of the automatic transmission 25) from the end portion on the right side in FIG.

  A plurality of notches 341 s are formed in the outer cylinder portion 341 a of the carrier body 341 so as to expose a part of the gear teeth formed on the outer periphery of each second pinion gear 33 b. The annular bottom portion 341b of the carrier body 341 has a plurality of shaft support holes 341o that support one ends 35a and 36a on the clutch C4 side (right side in FIG. 3) of the plurality of first and second pinion shafts 35 and 36, respectively. The plurality of shaft support holes 341o are formed in the annular bottom portion 341b so that the first and second pinion shafts 35 and 36 are alternately arranged in the circumferential direction, and the second pinion shaft 36 is positioned on the outer peripheral side of the first pinion shaft 35. It is formed.

  A clutch hub 51, which is one of the components of the clutch C4, is fixed to the surface on the clutch C4 side of the annular bottom portion 341b of the carrier body 341. As shown in FIG. 3, the clutch hub 51 extends from an outer peripheral portion of the annular flange portion 511 fixed to the annular bottom portion 341 b and the flange portion 511, and inner peripheral portions of the plurality of friction engagement plates 53. The spline to be fitted includes a cylindrical portion 512 formed on the outer peripheral surface. As shown in FIG. 3, the flange 511 of the clutch hub 51 is notched so that the shaft support hole 341o is exposed when viewed from the clutch C4 side at a position corresponding to the shaft support hole 341o of the carrier body 341. A plurality of cutout portions 511s are formed.

  The carrier cover 342 of the planetary carrier 34 is disposed so as to face the annular bottom 341 b of the carrier body 341. As shown in FIG. 3, the outer periphery of the carrier cover 342 is fixed to the end of the outer cylindrical portion 341a of the carrier body 341 opposite to the side where the annular bottom portion 341b is formed (the left side in FIG. 3). An inner peripheral portion of the cover 342 is fixed to the input shaft 26 of the automatic transmission 25. Thus, the carrier body 341 and the carrier cover 342 are integrated as a planetary carrier 34 and connected to the input shaft 26 of the automatic transmission 25. The carrier cover 342 has a plurality of shaft support holes 342o that support the other ends 35b, 36b on the opposite side (left side in FIG. 3) of the plurality of first and second pinion shafts 35, 36 to the clutch C4. .

  As shown in FIG. 3, shaft recesses 351a, 351a, which are recessed inward in the axial direction from the end surfaces, are respectively provided at one ends 35a, 36a of the first and second pinion shafts 35, 36 inserted through the shaft support holes 341o of the carrier body 341. 361a is formed. Further, the other ends 35b and 36b of the first and second pinion shafts 35 and 36 inserted into the shaft support hole 342o of the carrier cover 342 are shafts that are recessed inward in the axial direction from the end surfaces as shown in FIG. Concave portions 351b and 361b are formed.

  The first and second pinion shafts 35 and 36 have a part of the outer periphery that surrounds the shaft recesses 351a and 361a, and the outer periphery that surrounds the shaft recesses 351b and 361b while being caulked into the shaft support hole 341o of the annular bottom 341b of the carrier body 341. A part of the portion is fixed to the planetary carrier 34 by being caulked in the shaft support hole 342 o of the carrier cover 342. Thus, by fixing both of the first and second pinion shafts 35 and 36 and the planetary carrier 34 so that no backlash is formed, the first and second pinion shafts 35 and 36 and the planetary carrier 34 are fixed. Can be substantially integrated to further increase the rigidity of the planetary carrier 34.

  Next, the lubricating structure of the first planetary gear mechanism 30 will be described. As shown in FIG. 3, the first pinion shaft 35 includes an in-shaft oil passage 351 o extending from the shaft recess 351 a on the one end 35 a side toward the other end 35 b side, and a substantially central portion in the axial direction of the first pinion shaft 35. And an oil passage 352o extending in the radial direction from the oil passage 351o in the shaft and opening on the outer peripheral surface of the first pinion shaft 35. The second pinion shaft 36 has a shaft inner oil passage 361o extending from the shaft recess 361a on the one end 36a side toward the other end 36b side, and a diameter from the shaft inner oil passage 361o at a substantially central portion in the axial direction of the second pinion shaft 36. A radial oil passage 362o extending outward in the direction and opening on the outer peripheral surface of the second pinion shaft 36.

  Further, in the present embodiment, the inner cylinder portion 520 of the drum member 52 that supports the plurality of separator plates 54 and the pistons 55 of the clutch C4, the cancel plate 56 that defines the cancel oil chamber, and the like is more than the planetary carrier 34. A supply hole 100 is formed which is disposed close to the axis of one planetary gear mechanism 30 (the axis of the input shaft 26 of the automatic transmission 25) and connected to a hydraulic circuit of a lubricating system of a hydraulic control device (not shown). ing. The supply hole 100 rotatably supports the drum member 52 and is connected to the hydraulic control device via an oil passage 70o formed in the front support 70 fixed to the transmission case 22. As shown in FIG. 3, the supply hole 100 is formed so as to extend obliquely from the inner peripheral surface to the outer peripheral surface of the inner cylindrical portion 520 of the drum member 52 toward the first planetary gear mechanism 30 side. It has the opening part 100o formed so that it might overlap with the cyclic | annular bottom part 341b of the main body 341 and seeing from the radial direction of the 1st planetary gear mechanism 30. FIG.

  For the planetary carrier 39 of the first planetary gear mechanism 30, oil that flows out of the supply hole 100 and scatters around the planetary carrier 34 by the action of centrifugal force is collected and the first and second pinion shafts are collected. An annular oil receiver 60 that is supplied to the oil passages 351o and 361o in the shafts 35 and 36 is attached. The oil receiver 60 includes an annular portion 61 including a plurality of insertion portions 611 that are inserted into the in-shaft oil passages 351o and 361o of the corresponding first and second pinion shafts through the notch portions 511s of the clutch hub 51, and a supply The first planetary gear mechanism 30 and the annular portion 61 are disposed outside the hole 100 in the radial direction (hereinafter, simply referred to as “radial direction”) and formed radially inside the annular portion 61 and flow out of the supply hole 100. An annular oil receiving portion 62 that receives oil is supported by the planetary carrier 34 via the first and second pinion shafts 35 and 36.

  The annular portion 61 extends inside the cylindrical portion 512 of the clutch hub 51 and between the annular bottom portion 341b of the carrier body 341 and the cancel plate 56 of the clutch C4 when the oil receiver 60 is attached (as shown in FIG. 3). Exists. The surface of the annular portion 61 on the cancel plate 56 side is formed so as to be slidable with the cancel plate 56, whereby the oil receiver 60 is disposed between the first planetary gear mechanism 30 and the cancel plate 56. Also functions as a thrust washer. A plurality of grooves (not shown) for circulating oil as a lubricating medium are radially formed on the surface of the annular portion 61 on the cancel plate 56 side.

  The plurality of insertion portions 611 are inserted into the oil passages 351o and 361o in the shafts of the corresponding first and second pinion shafts 35 and 36 so as to be spaced from each other in the circumferential direction on the carrier body 341 side. The first planetary gear mechanism 30 and the annular portion 61 are extended in the axial direction (hereinafter simply referred to as “axial direction”) from the surface (left side in FIG. 3). An oil passage 611o extending in the axial direction is formed in each insertion portion 611 so as to communicate with the in-shaft oil passages 351o and 361o. The annular portion 61 is recessed from the inner peripheral surface toward the outer peripheral surface side so that oil flows (so as to collect the oil), and communicates with the oil passage 611o of the corresponding insertion portion 611. A plurality of oil collecting portions (independent oil collecting portions) 612 are formed at intervals in the circumferential direction. The oil collecting portion 612 is disposed on the radially outer side than the supply hole 100. In the present embodiment, the plurality of groove portions (not shown) on the surface of the annular portion 61 on the cancel plate 56 side are formed so as to extend between the oil collecting portions 612.

  The oil receiving portion 62 is a first planetary gear as it goes from the inner peripheral portion of the annular portion 61 on the carrier body 341 side toward the first and second pinion gears 33a, 33b (the opposite side to the annular portion 61: the left side in FIG. 3). An inclined portion having an inner peripheral surface 621a formed so as to be closer to the axis of the mechanism 30, that is, away from the axis of the first planetary gear mechanism 30 toward the annular portion 61 side (right side in FIG. 3). 621, an axially extending portion 622 extending in the axial direction from the inclined portion 621, and a regulating wall 623 formed so as to extend radially inward from one end of the axially extending portion 622 opposite to the inclined portion 621 including.

  As shown in FIG. 3, the inner peripheral surface 621 a of the inclined portion 621 is formed so as to extend from the annular portion 61 to the inside in the radial direction from the annular bottom portion 341 b of the carrier body 341 when the oil receiver 60 is attached. In addition, the inclined portion 621 has a contact surface 621b that extends in the radial direction on the carrier body 341 side relative to the inner peripheral surface 621a. The oil receiver 60 is attached to the planetary carrier 39 so that the contact surface 621b of the inclined portion 621 contacts the annular bottom portion 341b of the carrier body 341. The axially extending portion 622 is formed so as to extend along the inner peripheral surface of the annular bottom portion 341b of the carrier body 341 to a substantially central portion in the axial direction of the annular bottom portion 341b in the attached state of the oil receiver 60. However, the axially extending portion 622 may be formed to have a slight angle with respect to the axial direction.

  The restriction wall 623 is located slightly closer to the first and second pinion gears 33a and 33b than the center portion in the axial direction of the annular bottom portion 341b of the carrier body 341 in the attached state of the oil receiver 60, and the drum member of the clutch C4 52 extends radially inward from the axially extending portion 622 so that a clearance is formed between the inner cylindrical portion 520 and the inner cylindrical portion 520. However, the restriction wall 623 may be formed to have a slight angle with respect to the radial direction of the first planetary gear mechanism 30. The end surface of the regulating wall 623 on the inclined portion 621 side is located between both ends of the opening portion 100o of the supply hole 100 in the axial direction (between broken lines shown in FIG. 3). In this manner, a part of the axially extending portion 622 of the oil receiving portion 62 of the oil receiver 60 and the restriction wall 623 are open to the annular bottom portion 341b of the carrier body 341 and the supply hole 100 when the oil receiver 60 is attached. It is formed so as to be positioned between the portion 100o (so as to overlap the annular bottom portion 341b of the carrier main body 341 and the opening portion 100o of the supply hole 100 as viewed from the radial direction). However, the axially extending portion 622 and the supply hole 100 may be formed and arranged so that the entire axially extending portion 622 overlaps the opening 100o of the supply hole 100 when viewed from the radial direction.

  When the engine (not shown) is operated and the oil pump 24 is driven in the vehicle on which the power transmission device 20 configured as described above is mounted, the front of the lubricating system hydraulic circuit of the hydraulic control device (not shown) is driven. Oil (operating oil) as a lubricating medium is supplied to the supply hole 100 formed in the inner cylinder portion 520 of the drum member 52 of the clutch C4 via the oil passage 70o of the support 70, and flows out from the opening portion 100o. As described above, the supply hole 100 is formed so as to extend obliquely toward the first planetary gear mechanism 30 from the inner peripheral surface to the outer peripheral surface of the inner cylindrical portion 520 of the drum member 52. For this reason, the oil that has flowed out of the opening 100o of the supply hole 100 is caused by the centrifugal force to act on the annular bottom 341b side of the carrier body 341, and the first and second pinion gears 33a and 33b (and the sun gear of the first planetary gear mechanism 30). 31) Fly toward the side.

  As described above, the oil receiver 60 of the present embodiment has a planetary structure such that the axially extending portion 622 and the regulating wall 623 of the oil receiving portion 62 are positioned between the annular bottom portion 341b of the carrier body 341 and the supply hole 100. Attached to the carrier 34. As a result, the oil that flows out from the opening 100 o of the supply hole 100 and scatters toward the annular bottom 341 b is received by the axially extending portion 622 and the regulating wall 623 of the oil receiving portion 62. A part of the oil that flows out from the opening 100o of the supply hole 100 and scatters toward the first and second pinion gears 33a, 33b (and the sun gear 31) of the first planetary gear mechanism 30 extends in the axial direction. It is received by a restriction wall 623 extending radially inward from the portion 622. As described above, in the oil receiver 60, the oil receiving portion 62 formed on the radially inner side of the annular portion 61 can better receive the oil scattered in the portion separated from the oil collecting portion 612 of the annular portion 61. Can do.

  However, as described above, the end surface of the regulation wall 623 on the inclined portion 621 side is located between both ends of the opening portion 100o of the supply hole 100 in the axial direction. A clearance is provided between the regulation wall 623 and the inner cylinder portion 520 of the drum member 52. As a result, the amount of oil that flows out from the opening 100o of the supply hole 100 and is received by the oil receiving portion 62, and toward the first and second pinion gears 33a, 33b (and the sun gear 31) from the oil receiving portion 62. The amount of oil scattered can be adjusted more appropriately by the restriction wall 623. As a result, the oil as the lubricating medium is satisfactorily supplied also to the first and second pinion gears 33a and 33b of the first planetary gear mechanism 30, and the meshing portion between the first pinion gear 33a and the sun gear 31 and the second pinion gear 33b and the ring gear are supplied. It is possible to lubricate and cool the meshing part with 32 well.

  The oil received by the oil receiving portion 62 is guided to each oil collecting portion 612 of the annular portion 61 via the inner peripheral surface 621a of the inclined portion 621. In this way, the oil receiving portion 62 is formed with the inclined portion 621 having the inner peripheral surface 621a extending away from the axis of the first planetary gear mechanism 30 toward the annular portion 61 side. The oil can be smoothly guided from the axially extending portion 622 to the oil collecting portions 612 of the annular portion 61 via the inclined portion 621.

  Further, by forming an axially extending portion 622 extending in the axial direction between the regulating wall 623 and the inclined portion 621, the oil collected by the oil receiving portion 62 is temporarily stored in the axially extending portion 622. However, it is possible to evenly spread in the circumferential direction of the oil receiving portion 62 and more evenly guide the oil collecting portions 612 of the annular portion 61 formed at intervals in the circumferential direction. In particular, part of the axially extending portion 622 overlaps with the opening 100o of the supply hole 100 when viewed from the radial direction of the first planetary gear mechanism 30, so that the oil flowing out from the opening 100o is axially extended. Thus, the oil can be received more satisfactorily, and the oil can be distributed more uniformly and uniformly in the circumferential direction of the oil receiving portion 62.

  The oil guided into each oil collection portion 612 is passed through the oil passage 611o of each insertion portion 611 communicating with each oil collection portion 612, and the oil passage 351o in the shaft of the first and second pinion shafts 35, 36. , 361o, and further to the needle bearings 37, 38 via the radial oil passages 352o, 362o. Thereby, the needle bearings 37 and 38 can be better lubricated and cooled.

  The oil receiving portion 62 of the oil receiver 60 of the present embodiment includes an axially extending portion 622 extending in the axial direction between the inclined portion 621 and the restriction wall 623, but the axially extending portion 622 is an oil receiving portion. It may be omitted from the part 62. Further, the end surface of the regulating wall 623 on the inclined portion 621 side may be formed so as to be positioned closer to the first and second pinion gears 33a, 33b side than both ends of the opening portion 100o of the supply hole 100 in the axial direction. Further, the supply hole 100, a part of the axially extending portion 622 of the oil receiving portion 62 and the restriction wall 623 are configured so that at least oil that has flowed out from the supply hole 100 has an axially extending portion 622 or an inclined portion of the oil receiving portion 62. As long as they can be received at 621, they may not be arranged so as to overlap in the radial direction. In the present embodiment, a plurality of oil collecting portions (independent oil collecting portions) 612 are formed in the annular portion 61. However, the annular portion 61 is recessed from the inner peripheral surface toward the outer peripheral surface over the entire circumference. An oil collecting portion as a single annular recess may be formed.

  As described above, the oil receiver according to the present invention is supported by the planetary carrier of the planetary gear constituting the transmission, and from the supply hole disposed closer to the axis of the planetary gear than the planetary carrier. An annular oil receiver that collects oil that has flowed out and supplies the oil to an in-shaft oil passage of a pinion shaft that is inserted into a plurality of pinion gears supported by the planetary carrier, and is disposed radially outward from the supply hole. And an oil collecting portion formed so as to collect the oil, and a plurality of insertion portions inserted into the oil passage in the shaft and having an oil passage communicating with the oil collecting portion and the oil passage in the shaft. An annular portion including the outer circumferential portion and the outer side of the annular portion and the radially inner side of the annular portion, and receives oil flowing out of the annular portion. An annular oil receiving portion, and the oil receiving portion is formed so as to be closer to the shaft center from the annular portion toward the pinion gear side, and on the pinion gear side than the inclined portion. And a regulating wall formed to extend radially inward from the inclined portion.

  In the oil receiver configured as described above, at least a part of the oil that flows out from the supply hole arranged closer to the planetary gear shaft than the planetary carrier and scatters to the pinion gear side of the planetary gear is oil receiving portion. And is guided from the inclined portion to the oil collecting portion of the annular portion, and supplied to the oil passage in the shaft of the pinion shaft through the oil passage of the insertion portion communicating with the oil collecting portion. As described above, in this oil receiver, the oil receiving portion formed on the radially inner side of the annular portion better receives the oil scattered in the portion separated from the oil collecting portion of the annular portion, and the inclined portion. It is possible to smoothly lead to the oil collecting part of the annular part. Therefore, according to this oil receiver, the oil scattered around the planetary carrier can be better supplied to the oil passage in the shaft of the pinion shaft.

  The oil receiving portion may include an axially extending portion that extends in an axial direction of the planetary gear between the regulating wall and the inclined portion. Thereby, the oil collected by the oil receiving portion is spread evenly in the circumferential direction of the oil receiving portion by the axially extending portion, and the oil passages in the shafts are passed through the oil passages of the oil collecting portion and the plurality of insertion portions. Can lead to more evenly.

  Further, the inclined wall side end surface of the restriction wall may be positioned between both ends of the opening of the supply hole in the axial direction of the planetary gear, and at least a part of the axially extending portion is You may overlap with the said opening part of the said supply hole seeing from radial direction. As a result, the amount of oil that flows out from the opening of the supply hole and is received by the oil receiving portion, and the amount of oil that scatters to the pinion gear side from the oil receiving portion can be adjusted more appropriately by the restriction wall. As a result, the planetary pinion gear can be well lubricated and cooled. In addition, since at least a part of the axially extending portion overlaps the opening of the supply hole when viewed from the radial direction of the planetary gear, the oil flowing out from the opening of the supplying hole is well received by the axially extending portion. The oil can be distributed well and uniformly in the circumferential direction of the oil receiving portion.

  Further, the oil collection part may be composed of a plurality of independent oil collection parts formed at intervals in the circumferential direction, and the oil passages of the plurality of insertion parts are respectively associated with the corresponding independent oil collection parts. You may communicate with the said oil path in a shaft while connecting.

  And this invention is not limited to the said embodiment at all, and it cannot be overemphasized that a various change can be made within the range of the extension of this invention. Furthermore, the mode for carrying out the invention described above is merely a specific embodiment of the invention described in the column for solving the problem, and is described in the column for means for solving the problem. It is not intended to limit the elements of the invention.

  The present invention can be used in manufacturing industries such as an oil receiver and a transmission equipped with the same.

  20 power transmission device, 22 transmission case, 23 starting device, 23c lock-up clutch, 23d damper mechanism, 23o one-way clutch, 23p pump impeller, 23s stator, 23t turbine runner, 24 oil pump, 25 automatic transmission, 26 input shaft, 28 gear mechanism, 29 differential gear, 30 first planetary gear mechanism, 31 sun gear, 32 ring gear, 33a first pinion gear, 33b second pinion gear, 34 planetary carrier, 341 carrier body, 341a outer cylinder, 341b annular bottom, 341o, 342o Shaft support hole, 341s cutout, 342 carrier cover, 35 first pinion shaft, 35a, 36a one end, 35b, 36b other end, 351a, 351b, 361a, 3 1b Shaft recess, 351o, 361o Shaft oil passage, 352o, 362o Radial oil passage, 36 Second pinion shaft, 37, 38 Needle bearing, 40 Second planetary gear mechanism, 41a First sun gear, 41b Second sun gear, 42 Ring gear, 43a Short pinion gear, 43b Long pinion gear, 44 Planetary carrier, 51 Clutch hub, 511 Flange, 511s Notch, 512 Cylindrical part, 52 Drum member, 520 Inner cylindrical part, 53 Friction engagement plate, 54 Separator plate, 55 piston, 56 cancel plate, 60 oil receiver, 61 annular portion, 611 insertion portion, 611o oil passage, 612 oil collecting portion, 62 oil receiving portion, 621 inclined portion, 621a inner peripheral surface, 621b contact surface, 622 axial Extending portion 623 restricting wall 70 front support, 70 o oil passage 100 supply hole, 100o opening, B1, B2 brake, C1, C2, C3, C4 clutch, F1 the one-way clutch.

Claims (2)

It is supported by the planetary carrier of the planetary gear constituting the transmission, and also collects the oil flowing out from the supply hole arranged closer to the planetary gear shaft than the planetary carrier and supports it by the planetary carrier. In the annular oil receiver that supplies the oil passage in the shaft of the pinion shaft inserted through the plurality of pinion gears,
An oil collecting portion that is disposed radially outside the supply hole and that is configured to collect the oil, and an oil passage that communicates with the oil collecting portion and the oil passage in the shaft, and in the shaft An annular portion including a plurality of insertion portions to be inserted into the oil passage;
An annular oil receiving portion that is formed radially outside the supply hole and radially inward of the annular portion, and receives the oil flowing out from the supply hole;
The oil receiving portion is inclined so as to be closer to the shaft center from the annular portion toward the pinion gear, and extends more radially inward than the inclined portion on the pinion gear side than the inclined portion. and it formed restricting wall as, seen including an axial extending portion extending in the axial direction of the planetary gear between the regulating wall and the inclined portion,
An end surface of the regulation wall on the inclined portion side is located between both ends of the opening portion of the supply hole in the axial direction of the planetary gear ,
At least a part of the axially extending portion overlaps with the opening of the supply hole when viewed from the radial direction . The oil receiver according to claim 1 ,
The oil collecting part is composed of a plurality of independent oil collecting parts formed at intervals in the circumferential direction,
The oil passages of the plurality of insertion portions communicate with the corresponding independent oil collection portions and the oil passages in the shaft, respectively.

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