JP2004132440A - Lubricating structure of power transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve lubrication in a device even under restriction of arranging bearings and constitutional restriction by miniaturization of a transmission in a power transmission. <P>SOLUTION: This power transmission stops revolution of a carrier C of a planetary gear set 2, and rotates a ring gear R2 when pinions P1 and P2 supported by the carrier C autorotate, and has an oil passage for lubricating the pinions P1 and P2 via an oil passage 24 of the carrier C and supplying lubricating oil to the oil passage 24 via a shaft 20 nearer to the center than a wall from the wall 21. The oil passage makes a space 26 for delivering the lubricating oil to the shaft 20 from the wall 21 by mutual surfaces opposed in the axial direction of the shaft 20 and the wall 21. The bearings 30 and 31 for supporting the ring gear R2 are positioned on a block 29 arranged in the carrier C adjacently to an end part on the opposite side of the side adjacent to the oil passage 24 of a pinion shaft 23, and the block 29 is provided with lubricating oil passages 29a and 29b for introducing the lubricating oil supplied to the oil passage 24 to the bearings 30 and 31. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a power transmission device having a specific motion state in which a pinion gear supported by a carrier of a planetary gear mechanism stops rotating and a ring gear meshing with the pinion gear rotates. The present invention relates to a lubrication structure for improving lubrication of lubricating oil in the device.
[0002]
[Prior art]
In a power transmission device having a planetary gear mechanism, in a structure in which a rotatably supported carrier supports a pinion shaft, the pinion shaft supports a pinion gear, and a ring gear meshes with the pinion gear. In addition, the ring gear bearing that rotatably supports the ring gear also requires sufficient lubrication of the pinion gear and the ring gear bearing to prevent seizure. In this regard, there has been a conventional automatic transmission having a structure in which the pinion gear and the ring gear bearing can be sufficiently lubricated in all the shift speeds by a pumping action of an output member that is constantly rotating except when the automatic transmission is stopped, for example, Reference 1).
[0003]
[Patent Document 1]
JP 07-208586 A
[Problems to be solved by the invention]
By the way, in the above automatic transmission, the rotation of the pinion gear is also stopped while the rotation of the wheels is stopped. Therefore, it is not necessary to lubricate the pinion gear and the ring gear bearing of the gear transmission while the rotation of the wheels is stopped in the automatic transmission.
[0005]
However, for example, in a hybrid transmission, when a motor such as an engine and a motor / generator are mounted, and the engine is rotated in a vehicle stopped state, that is, the rotation of the wheels is stopped, the motor / generator is rotated to generate power. There is. When the vehicle is stopped, the planetary gear mechanism of the hybrid transmission stops rotating the carrier finally connected to the wheels, but the pinion gear and the ring gear rotate with the rotation of the sun gear nearby. Become.
[0006]
Therefore, even when the vehicle is stopped, it is necessary to lubricate the rotating pinion gear and the ring gear bearing. However, since the rotation of the output member such as a carrier disposed around the pinion gear is stopped, the pump function cannot be used. By the way, in order to use the lubricating oil for cooling the motor / generator, it is conceivable to configure the hybrid transmission so that the lubricating oil supply pressure is made extremely low so that only the oil necessary for cooling flows. In this case, if the lubricating oil is branched from the oil passage for cooling the motor / generator and guided to the oil passage of the carrier, it is difficult to raise the oil upward even if a direct throttle is provided. It is assumed that it becomes extremely difficult to send the lubricating oil to the pinion gear located on the upper side. Therefore, it is extremely difficult to sufficiently lubricate the pinion gear and the ring gear bearing located on the upper side under the condition that the amount of lubricating oil is small and the pressure is low while the rotation of the wheel is stopped. Otherwise, seizure of the pinion gear and the ring gear bearing may occur.
[0007]
In order to solve such a problem, it is conceivable to change the configuration such as the arrangement of the members. However, there are structural reasons such as restriction on the arrangement of the bearings and downsizing of the transmission. It is difficult to sufficiently lubricate the pinion gear and the ring gear bearing located above the axis of the carrier.
[0008]
In addition, the lubricating oil is usually supplied to the rotating member having a large inflow resistance due to the interposition of the bush, and the lubricating oil is guided to the shaft center of the rotating member via the transfer portion in the rotating member, and is transmitted from the lubricating oil passage of the shaft center. A configuration is also conceivable in which the lubricating oil is branched and guided to the carrier, and the lubricating oil is guided to a pinion gear or a ring gear bearing located above the axis of the carrier by hydraulic pressure due to centrifugal force generated by rotation of the rotating member. However, when the lubricating oil supply oil pressure is low and the rotating member is not rotating or the rotation speed is low, there is a problem that the amount of lubricating oil to the upper pinion gear and the ring gear bearing is insufficient.
[0009]
In view of the above, the present invention advantageously solves the above problem, and when the revolving of the carrier of the planetary gear mechanism is stopped, the pinion gear supported by the carrier rotates and the ring gear meshing with the pinion gear rotates. In a power transmission device in which a specific motion state exists, the lubricating oil in the device can be controlled regardless of the rotation of the rotating member even under the restriction of the arrangement of the bearings and the restriction of the configuration due to the downsizing of the transmission. The purpose is to improve the supply.
[0010]
[Means for Solving the Problems]
The lubricating structure of the power transmission device according to the present invention has the following features.
The present invention relates to a power transmission in which there is a motion state in which the revolution of a carrier of a planetary gear mechanism is stopped, and a pinion gear supported on a pinion rotating shaft provided on the carrier rotates by itself and a ring gear meshing with the pinion gear rotates. The lubrication structure of the device is assumed.
According to the present invention, the lubrication structure of the power transmission device lubricates the bearing of the pinion gear through the oil passage of the carrier and the oil passage of the pinion rotation shaft connected thereto, and further moves the fixed wall from the fixed wall to the center. A lubricating oil passage for supplying lubricating oil to the oil passage of the carrier via a closer rotating member, wherein the lubricating oil passage is formed between surfaces of the rotating member and the fixed wall which face each other in the axial direction of the rotating member. By this, a space that passes the lubricating oil from the fixed wall to the rotating member is defined, and a ring gear bearing that supports the ring gear is an end portion of the pinion rotation shaft opposite to a side adjacent to an oil passage of the carrier. The lubricating oil supplied to the oil passage of the pinion rotation shaft is located on a block provided on the carrier adjacent to the ring gear bearing. And includes a ring gear bearing lubricating oil passage that leads.
[0011]
【The invention's effect】
According to the lubrication structure of the power transmission device of the present invention having the above-described configuration, the lubricating oil passage that supplies the lubricating oil to the oil passage of the carrier from the fixed wall via the rotating member closer to the center of the fixed wall is formed by the rotating member and the rotating member. The surfaces of the rotating member and the fixed wall that oppose each other in the axial direction define a space that transfers the lubricating oil from the fixed wall to the rotating member. Thereby, the lubricating oil supply oil pressure is increased by branching the oil passage from the upstream side where the lubricating oil supply oil pressure is higher than branching from the oil passage along the axis of the rotating member and guiding the lubricating oil to the carrier oil passage. Can be. Therefore, the lubricating oil can be sufficiently supplied from the oil passage of the carrier to the pinion gear via the oil passage of the pinion rotating shaft without using the pump action by the rotation of the peripheral members of the pinion gear. From the oil passage of the shaft, through a ring gear bearing lubricating oil passage provided by a block provided in the carrier adjacent to the end of the pinion rotating shaft opposite to the side adjacent to the oil passage of the carrier, and on the block. , The lubricating oil can be sufficiently supplied to the ring gear bearing that supports the ring gear, so that even when the vehicle is stopped, the pinion gear positioned above the axis of the stopped carrier. And the ring gear bearing can be sufficiently lubricated.
[0012]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 illustrates a hybrid transmission as a power transmission device to which the lubrication structure of the power transmission device of the present invention is applied. In the present embodiment, this is a transformer for a front-wheel drive vehicle (FF vehicle). The structure described below is useful for use as an axle.
[0013]
In FIG. 1, reference numeral 1 denotes a transmission case, and a Ravigneaux type planetary gear set 2 as a planetary gear mechanism is built in the transmission case 1 on the right side in the axial direction (the left-right direction in the figure) (front side near the engine ENG). On the left side of FIG. 1 (on the rear side far from the engine ENG), for example, a motor / generator set that enables the composite current two-layer motor 4 is incorporated.
The Ravigneaux type planetary gear set 2 and the composite current two-layer motor 4 are coaxially arranged on the main axis of the transmission case 1, but the countershaft 5 and the differential gear device 6, which are offset from the main axis and arranged in parallel, also change the speed. It is built into the machine case 1.
[0014]
The Ravigneaux type planetary gear set 2 is a combination of a single pinion planetary gear set 7 and a double pinion planetary gear set 8 sharing a long pinion (pinion gear) P1. The single pinion planetary gear set 7 has a structure in which a long pinion P1 is meshed with a sun gear S2 and a ring gear R1. The double-pinion planetary gear set 8 includes a large-diameter short pinion (pinion gear) P2 in addition to the sun gear S1, the long pinion P1, and the ring gear R2. The short pinion P2 meshes with the sun gear S1 and the long pinion P1, and the ring gear R2. And a structure in which it is also meshed.
Note that the Ravigneaux planetary gear set 2 has a configuration in which a total of six pinion gears, that is, three long pinions P1 and three short pinions P2 are provided.
Then, all the pinion gears P1, P2 of the planetary gear sets 7, 8 are rotatably supported by a common carrier C.
The forward brake FWD / B composed of a multi-plate brake acts to restrain the rotation of the ring gear R2 by engaging the forward brake FWD / B. The forward brake FWD / B is always engaged when the vehicle travels forward, while it is engaged when the vehicle travels backward. The fastening is released.
[0015]
The Ravigneaux-type planetary gear set 2 having the above-described configuration mainly includes five rotating members of a sun gear S1, a sun gear S2, a ring gear R1, a ring gear R2, and a carrier C, and two members among the five rotating members. Is determined, the rotational speed of the other members is determined, and a two-degree-of-freedom differential is determined.
The rotation speeds of the five rotating members are in the order of the sun gear S1, the ring gear R1, the carrier C, the ring gear R2, and the sun gear S2.
[0016]
The composite current two-layer motor 4 also includes an inner rotor 4ri and an annular outer rotor 4ro surrounding the inner rotor 4ri, supported coaxially and rotatably in the transmission case 1. The inner rotor 4ri and the outer rotor 4ro are provided. An annular stator 4s coaxially arranged in an annular space between them is fixed to the transmission case 1.
A first motor / generator MG1, which is an inner motor / generator, is constituted by the annular coil 4s and the inner rotor 4ri, and a second motor / generator MG2, which is an outer motor / generator, is constituted by the annular coil 4s and the outer rotor 4ro. Is configured.
Here, the motor / generators MG1 and MG2 are motors that output rotations in respective directions according to the supply current when supplied with the composite current and at respective speeds (including stop) according to the supply current. It functions as a generator that generates electric power according to the rotation due to external force when the composite current is not supplied.
[0017]
The five rotating members of the Ravigneaux type planetary gear set 2 include a first motor / generator MG1 and an engine ENG as a prime mover in the order of sun gear S1, ring gear R1, carrier C, ring gear R2 and sun gear S2 in order of rotational speed. The output (Out) to the wheel drive system including the differential gear device 6, the forward brake FWD / B, and the second motor / generator MG2 are respectively coupled.
[0018]
This coupling will be described in detail below with reference to FIG. 1. In order to use the ring gear R1 as an input element to which the engine (ENG) rotation is input as described above, the ring gear R1 is connected to the engine crankshaft 9 via the clutch CL. Join.
The clutch CL here disconnects and connects the ring gear R <b> 1 and the engine crankshaft 9. By the connection and disconnection of the clutch CL, dragging of the engine torque during the electric running, which should be performed only by the motor / generator while the engine is stopped, can be prevented.
The sun gear S1 is coupled to the inner rotor 4ri of the first motor / generator MG1 via the hollow shaft 13, and the sun gear S2 is connected to the second motor / generator MG2 via the shaft 14 into which the motor / generator MG1 and the hollow shaft 13 are loosely fitted. To the outer rotor 4ro.
[0019]
In order to make the carrier C an output element for outputting rotation to the wheel drive system as described above, an output gear 16 is connected to the carrier C via a hollow shaft 15 and meshed with a counter gear 17 on the counter shaft 5. Let it.
A final drive pinion 18 is separately provided integrally with the counter shaft 5 and meshes with a final drive ring gear 19 provided in the differential gear device 6.
The output rotation from the transmission reaches the differential gear device 6 via a final drive gear set constituted by a final drive pinion 18 and a final drive ring gear 19, and is distributed to the left and right tires T by the differential gear device. .
[0020]
In the hybrid transmission having the above configuration, as described above, the engine / ENG is rotated in the vehicle stopped state, that is, in the stopped state of the rotation of the tire T as the wheel shown in FIG. May be rotated to generate power. When the vehicle is stopped, the Ravigneaux-type planetary gear set 2 stops the revolution of the carrier C finally connected to the tire T, and rotates the sun gears S1 and S2 and the ring gear R1 to rotate the pinion gear P1 supported by the carrier C. , P2 rotates and the ring gear R2 meshing with the pinion gear P2 also rotates.
[0021]
Therefore, in the present embodiment, even in such a stopped state of the vehicle, the lubrication of the pinion gears P1 and P2 supported by the carrier C and the bearing rotatably supporting the ring gear R2 meshing with the pinion gear P2 can be sufficiently performed. Applies the following lubrication structure to the hybrid transmission.
[0022]
Here, FIG. 2 is a sectional view showing a lubricating structure applied to the hybrid transmission having the above-described configuration in an actual configuration, and FIG. 3 is a partially enlarged sectional view of the actual configuration shown in FIG. In this actual configuration, an input shaft 20 as a rotating member is interposed between the shaft 14 and the engine crankshaft 9, and one end of the input shaft 20 is connected to the engine crankshaft 9 while the input shaft 20 The other end is connected to the shaft 14.
[0023]
Further, in this actual configuration, it is necessary to provide a needle bearing 27 as a bearing for supporting the force in the thrust direction of the input shaft 20 near the inner peripheral end of the fixed wall 21, as will be described in detail later. The layout is configured to reduce the size of the transmission.
[0024]
In the lubricating structure of the present embodiment, as shown in FIGS. 2 and 3, the lubricating oil flowing from the transmission case 1 flows radially inward through the fixed wall 21 fixed to the transmission case 1. An upstream lubricating oil passage 21a is provided. Further, a radially inner portion of the upstream-side lubricating oil passage 21a is provided with an axial supply oil passage 21b opening on the inner peripheral surface of the fixed wall 21 and an axial direction extending in the axial direction and opening on an end surface of the fixed wall 21. It branches to the lubricating oil passage 21c.
[0025]
The input shaft 20 has a flange 20a facing the fixed wall 21 and is arranged closer to the center of the transmission than the fixed wall 21 is. An axial oil passage 20b is provided at the axis of the input shaft 20. The shaft oil passage 20b communicates with a shaft oil passage 14a provided at the shaft center of the shaft 14, and supplies oil for cooling the motor / generators MG1 and MG2 shown in FIG. 1 and lubricating each member. Do. In addition, the input shaft 20 is provided with a first radial lubricating oil passage 20c that transfers lubricating oil from the outside in the radial direction of the input shaft 20 to the axial oil passage 20b. The lubricating oil is guided from the axial supply oil passage 21 b of the fixed wall 21 to the first radial lubricating oil passage 20 c of the input shaft 20 via a bush 22.
[0026]
Further, the input shaft 20 is provided with a carrier communication oil passage 20d and a second radial lubrication oil passage 20e. The carrier communication oil passage 20 d guides the lubricating oil flowing into the thrust bearing 27 disposed in the space 26 to the carrier C. In addition, the second radial lubricating oil passage 20e is formed on the inner peripheral surface near the corner on the fixed wall 21 side formed by the flange 20a and the shaft portion, with the axial oil passage 20b along the axis and the space 26. It is provided in communication. Note that the second radial lubricating oil passage 20e has a flow passage cross-sectional area smaller than that of the first radial lubricating oil passage 20c, thereby increasing the flow passage resistance more than the first radial lubricating oil passage 20c. I have.
[0027]
The carrier C of the Ravigneaux type planetary gear set 2 is provided with a pinion rotation shaft supply oil passage 24 which communicates with the pinion gear lubrication oil passage 23a of the pinion rotation shaft 23 of each pinion gear (long pinion P1, short pinion P2). Lubricating oil is supplied to the roller bearings that rotatably support the pinion gears P1 and P2 from the pinion gear lubricating oil passage 23a of the pinion rotating shaft 23 through the path, and the lubricating oil is supplied to the pinion gears P1 and P2 from there. The lubricating oil is guided from the carrier communication oil passage 20d of the input shaft 20 to the pinion rotation shaft supply oil passage 24 of the carrier C via a bush 25 pressed into the carrier C.
[0028]
Further, a space 26 is defined by surfaces of the flange 20a of the input shaft 20 and the fixed wall 21 which face each other in the axial direction of the input shaft 20, and a portion from the center of the space 26 is formed as described above. A needle bearing 27 for supporting a thrust force of the input shaft 20 is provided. On the other hand, in a portion on the outer peripheral side of the space 26, oil leakage is prevented by a seal of an oil passage for the clutch CL provided on the input shaft 20. The bearing 27 for supporting the thrust force of the input shaft 20 may be a bearing other than a needle bearing.
[0029]
Therefore, according to such a lubrication structure, as shown in FIG. 3, with respect to lubrication of the pinion gears P1 and P2 supported by the carrier C, when the input shaft 20 rotates at a low speed, the upstream side of the transmission case 1 and the fixed wall 21. The oil flowing into the side lubricating oil passage 21a flows into the axial supply oil passage 21b and the axial lubricating oil passage 21c as indicated by arrows A1 and A2. The oil flowing into the shaft supply oil passage 21b as shown by the arrow A2 flows from the first radial lubricating oil passage 20c through the bush 22 to the shaft oil passage 20b. As shown, it flows into the shaft oil passage 14a, which is the main oil passage, to cool motor / generators MG1 and MG2 (not shown in FIG. 3) and lubricate each part.
Here, the oil guided from the shaft oil passage 14a and cooling the motor / generators MG1 and MG2 is returned to the oil passage outside the outer periphery of the shaft 14 again to lubricate the members.
[0030]
On the other hand, the oil that has flowed into the axial lubricating oil passage 21c flows from the axial lubricating oil passage 21c through the space 26 into the carrier communication oil passage 20d and the second radial lubricating oil passage 20e of the input shaft 20. . At this time, the lubricating oil flows from the space 26 into the carrier communication oil passage 20d as shown by an arrow A4 from the outside to the inside of the needle bearing 27 disposed in the space 26, and from there, the carrier communication oil passage. Flow into 20d. Further, the oil that has flowed into the carrier communication oil passage 20d flows into the pinion rotation shaft supply oil passage 24 of the carrier C via the bush 25 as shown by an arrow A5, and from there, as shown by an arrow A6. Through the pinion gear lubricating oil passage 23a of the rotating shaft 23, it is supplied to the roller bearings supporting the pinion gears P1 and P2, and further to the pinion gears P1 and P2. The oil flowing from the space 26 into the second radial lubricating oil passage 20e flows into the axial oil passage 20b to cool the motor / generators MG1 and MG2 and lubricate each part in the same manner as described above. Do.
[0031]
Therefore, when the lubricating oil is supplied from the fixed wall 21 to the input shaft 20 at the time of low rotation of the input shaft 20, the lubricating oil is larger than the radially outer portion of the input shaft 20 having the large inflow resistance due to the interposition of the bush 22. The lubricating oil is delivered to the input shaft 20 via the space 26 from the axial lubricating oil passage 21c branched from the upstream side where the supply oil pressure is high, and the pinion gears P1 and P2 are lubricated via the pinion rotation shaft supply oil passage 24 of the carrier C. Therefore, the lubricating oil is supplied to the pinion rotary shaft supply oil passage 24 of the carrier C at a higher lubricating oil supply oil pressure than the shaft oil passage 20b of the input shaft 20. Lubricating oil can be sufficiently supplied to the pinion gear.
[0032]
On the other hand, when the input shaft 20 rotates at a high speed, in the space 26 between the input shaft 20 and the fixed wall 21, as the wall of the input shaft 20 rotates at a high rotation speed, the needle roller of the needle bearing 27 also becomes a half thereof. It rotates at the number of rotations. Therefore, when the input shaft 20 rotates at a high speed, a centrifugal force acts on the oil in the space 26, and there is a possibility that the centrifugal force prevents the inflow of the lubricating oil from the axial lubricating oil passage 21c into the space 26. is there. However, in this case, the oil flowing into the shaft oil passage 20b from the upstream lubricating oil passage 21a via the shaft supply oil passage 21b (including the oil blocked from flowing into the space 26) is subjected to centrifugal force. Accordingly, the oil flows from the shaft center oil passage 20b to the second radial lubrication oil passage 20e. In addition, since the centrifugal force due to the rotation of the input shaft 20 does not act at the time of low rotation, the lubricating oil is less likely to flow into the second radial lubricating oil passage 20e having a larger inflow resistance than the first radial lubricating oil passage 20c. I have.
[0033]
Therefore, according to the lubricating structure of the present embodiment, when the input shaft 20 rotates at a high speed, as shown by the arrow A7, the space 26 extends from the axial oil passage 20b through the second radial lubricating oil passage 20e. Flows into the inside of the needle bearing 27 disposed in the shaft, and through the carrier communication oil passage 20d and the pinion rotation shaft supply oil passage 24 of the carrier C as described above, lubricating oil flows to the roller bearings supporting the pinion gears P1 and P2. Is supplied. As a result, a sufficient amount of lubricating oil is supplied to the pinion rotary shaft supply oil passage 24 of the carrier C, so that even when the input shaft 20 rotates at a high speed, sufficient lubricating oil is supplied to the pinion gears P1 and P2 located above. Can be supplied.
[0034]
In the lubrication structure of the hybrid transmission according to the present embodiment, the end of the pinion rotation shaft 23 on the opposite side to the side adjacent to the pinion rotation shaft supply oil passage 24 of the carrier C (the left end in the figure) Portion), a ring-shaped block 29 is provided on the carrier C, and needle bearings 30, 31 as ring gear bearings for rotatably supporting the ring gear R2 in the thrust direction are arranged on the small diameter portion of the block 29. The block 29 is provided with a gallery (oil reservoir) 29a as a ring gear bearing lubricating oil passage and a fine oil lubricating oil passage for guiding the lubricating oil supplied to the pinion gear lubricating oil passage 23a of the pinion rotating shaft 23 to the needle bearings 30, 31 of the ring gear R2. A gallery 29a which has a radial oil passage 29b and partially extends in the circumferential direction of the block 29 is lubricated. Oil once the reservoir is in calibration, supplied to the needle bearing 30 and 31 from the small-diameter oil passage 29b.
[0035]
The block 29 is formed separately from the carrier C and is integrally fixed to the carrier C. Before the block 29 is fixed to the carrier C, an inner peripheral portion of the block 29 is provided with an output shaft coupled to the output gear 16. A spline for transmitting power to the hollow shaft 15 is formed, and a gallery 29a and a small-diameter oil passage 29b are formed inside the block 29. The block 29 is closely fitted to and fixed to the carrier C. Then, the end of the pinion rotation shaft 23 opposite to the side adjacent to the pinion rotation shaft supply oil passage 24 is supported by the carrier C with a slight gap from the block 29, and fixed to the carrier C with the pins 28. are doing.
[0036]
As described above, in the lubrication structure of the hybrid transmission according to the present embodiment, the lubrication of the pinion gears P1 and P2 via the pinion rotation shaft supply oil passage 24 of the carrier C and the fixing of the lubrication from the fixed wall 21 are performed. Lubricating oil passages 21a, 21c, and 20d are provided for supplying lubricating oil to the pinion rotary shaft supply oil passage 24 via the input shaft 20 closer to the center than the wall. The lubricating oil passage defines a space 26 for passing the lubricating oil from the fixed wall 21 to the input shaft 20 by surfaces of the input shaft 20 and the fixed wall 21 that face each other in the axial direction of the input shaft 20. I have.
[0037]
Therefore, according to the lubricating structure of the hybrid transmission of the present embodiment having the above-described configuration, the lubricating oil is branched from the shaft oil passage 20 b along the axis of the input shaft 20 to the pinion rotary shaft supply oil passage 24 of the carrier C. The lubricating oil supply hydraulic pressure is increased by supplying the lubricating oil to the pinion rotary shaft supply oil passage 24 of the carrier C by the axial lubricating oil passage 21c which is branched from the upstream side where the lubricating oil supply oil pressure is higher than the oil supply hydraulic pressure. Can be enhanced. Thereby, even without using the pumping action by the rotation of the peripheral members of the pinion gears P1 and P2, the pinion rotation shaft supply oil passage 24 of the carrier C to the pinion gears P1 and P2, and from the pinion rotation shaft supply oil passage 24, Lubricating oil can be sufficiently supplied to the needle bearings 30 and 31 as ring gear bearings via the gallery 29a as the ring gear bearing lubricating oil passage and the small diameter oil passage 29b. Therefore, even when the vehicle is stopped, the pinion gears P1, P2 and the needle bearings 30, 31 located above the axis of the stopped carrier C can be sufficiently lubricated.
[0038]
Further, according to the lubricating structure of the hybrid transmission according to the present embodiment having the above-described configuration, the block 29 is formed separately from the carrier C and fixed integrally to the carrier C. A spline for transmitting power to the hollow shaft 15 as an output shaft, a gallery 29a and a small-diameter oil passage 29b can be easily formed therein, and the lubrication measured to the minimum necessary in the gallery 29a. The oil can be sent to the needle bearings 30 and 31, and a sufficient amount of lubricating oil can be sent to the pinion gears P1 and P2.
[0039]
Further, according to the lubricating structure of the hybrid transmission of the present embodiment having the above configuration, the block 29 is brought into close contact with the carrier C, and the pinion rotary shaft 23 is located on the opposite side to the side adjacent to the pinion rotary shaft supply oil passage 24. Since the end portion is supported by the carrier C with a gap from the block 29, the block 29 can be securely brought into close contact with the carrier C without interference of the pinion rotating shaft 23, and leakage of lubricating oil from between them can be ensured. Can be prevented.
[0040]
In order to minimize the radius of a portion of the input shaft 20 where an oil passage for supplying lubricating oil from the carrier C to the pinion rotary shaft 23 is provided, the layout is made smaller than that of the axial lubricating oil passage 21c. It is advantageous to arrange the carrier communication oil passage 20d radially inward. However, in this case, since the centrifugal force applied to the lubricating oil increases as the rotation speed of the input shaft 20 increases, the supply amount of the lubricating oil to the carrier communication oil passage 20d decreases, and the flow may stop at a high rotation speed. There is. On the other hand, in the lubricating structure of the hybrid transmission according to the present embodiment, the lubricating oil is transferred from the radial direction of the input shaft 20 to the shaft oil passage 20b along the axis of the input shaft 20. From there, a second radial lubricating oil passage 20e with a large resistance is provided, which lubricates each part in the hybrid transmission and connects the shaft center oil passage 20b and the space 26.
[0041]
Therefore, according to the lubricating structure of the hybrid transmission of the present embodiment having the above configuration, when the input shaft 20 rotates at a high speed, the centrifugal force causes the second radial lubricating oil passage from the axial oil passage 20b of the input shaft 20. The lubricating oil can be sufficiently supplied to 20e. Accordingly, the supply amount of the lubricating oil to the pinion rotary shaft supply oil passage 24 of the carrier C can be increased, and the pinion gears P1, P2 and the needle bearings 30, The pressure of the oil passage for supplying the lubricating oil to 31 can be increased.
[0042]
Moreover, in the lubricating structure of the hybrid transmission according to the present embodiment, a needle bearing 27 that supports a thrust force of the input shaft 20 is provided in the space 26. As a result, the space 26 serves as both a space for disposing the needle bearing 27 and an oil passage for lubricating oil, so that space efficiency can be improved and lubricating oil passages to the pinion gears P1, P2 and the needle bearings 30, 31 are formed. In this case, it is possible to prevent the transmission from being lengthened in the axial direction.
[0043]
As described above, the present invention has been described based on the illustrated examples, but the present invention is not limited to the above examples. For example, in the above embodiment, the lubrication structure of the power transmission device of the present invention is applied to the hybrid transmission. However, the motion state in which the revolution of the carrier of the planetary gear mechanism stops and the pinion gear supported by the carrier rotates on its own axis. Any existing power transmission device can be applied.
[Brief description of the drawings]
FIG. 1 is a schematic configuration diagram illustrating a hybrid transmission to which a lubrication structure according to the present invention can be applied.
FIG. 2 is an actual configuration diagram showing a lubrication structure of a hybrid transmission as a main part of the present embodiment based on the schematic configuration diagram.
FIG. 3 is a partially enlarged sectional view of the actual configuration diagram shown in FIG. 2;
[Explanation of symbols]
1 Transmission case 2 Ravigneaux type planetary gear set (differential device)
ENG engine (motor)
Reference Signs List 4 combined current two-layer motor MG1 first motor / generator MG2 second motor / generator 7 single pinion planetary gear set 8 double pinion planetary gear set 9 engine crankshaft 14 shaft 14a shaft center oil passage 20 input shaft (rotating member)
20a Flange 20b Axial oil passage 20c First radial lubricating oil passage 20d Carrier communicating oil passage 20e Second radial lubricating oil passage 21 Fixed wall 21a Upstream lubricating oil passage 21b Axial supply oil passage 21c Axial lubricating oil Path 22 Bush 23 Pinion rotation shaft 23a Pinion gear lubrication oil passage 24 Pinion rotation shaft supply oil passage 25 Bush 26 Space 27 Needle bearing 28 Pin 29 Block 29a Gallery 29b Small diameter oil passage 30 Needle bearing 31 Needle bearing S1 Sun gear S2 Sun gear P1 Long pinion P2 Short pinion C Carrier R Ring gear CL Clutch T Tire

Claims (3)

A lubricating structure for a power transmission device in which a revolving motion of a carrier of a planetary gear mechanism stops, and a pinion gear supported on a pinion rotating shaft provided on the carrier rotates and a ring gear meshing with the pinion gear rotates. At
Lubricating the pinion gear through the oil passage of the carrier and the oil passage of the pinion rotation shaft connected thereto, and lubricating oil to the oil passage of the carrier from a fixed wall through a rotating member closer to the center than the fixed wall. Equipped with a lubricating oil passage for supplying
The lubricating oil passage defines a space for passing the lubricating oil from the fixed wall to the rotating member by surfaces of the rotating member and the fixed wall that face each other in the axial direction of the rotating member,
A ring gear bearing that supports the ring gear is located on a block provided on the carrier adjacent to an end of the pinion rotation shaft opposite to a side adjacent to an oil passage of the carrier,
The lubricating structure of a power transmission device, wherein the block includes a ring gear bearing lubricating oil passage that guides lubricating oil supplied to an oil passage of the pinion rotating shaft to the ring gear bearing. The lubricating structure for a power transmission device according to claim 1,
The block is formed separately from the carrier and is integrally fixed to the carrier,
The block further comprises a spline for transmitting power to an output shaft of the planetary gear mechanism, and a gallery for measuring and supplying lubricating oil to the ring gear bearing in the ring gear bearing lubricating oil passage. Transmission device lubrication structure. The lubricating structure for a power transmission device according to claim 2,
The block is brought into close contact with the carrier, and an end of the pinion rotation shaft on the side opposite to the side adjacent to the oil passage of the carrier is supported by the carrier with a gap provided with respect to the block, Power transmission device lubrication structure.

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