JP5136401B2 - Lubricating structure of planetary gear mechanism - Google Patents

Description

  The present invention relates to a lubricating structure for a planetary gear mechanism. In particular, the present invention relates to a lubricating structure of a planetary gear mechanism used in a transmission of a hybrid vehicle in which an engine and a motor are used as power sources.

  A conventional transmission mounted on a vehicle includes a sun gear that is rotatably provided, a planetary gear that can revolve around the sun gear centering on the center of rotation of the sun gear and a planetary gear that rotates while meshing with the sun gear. A carrier that supports the planetary gear so that it can revolve around the sun gear, and a ring gear whose rotation center is the same rotation center as the rotation center of the sun gear and that can rotate around the planetary gear while meshing with the planetary gear Some planetary gear mechanisms having the following are used. This planetary gear mechanism can transmit the power from the engine, which is a power source, to the drive wheel side at a desired gear ratio by controlling the rotation of the sun gear, carrier, etc. using a clutch or a brake.

  Also, in such a planetary gear mechanism, lubricating oil is usually supplied by an oil pump that operates during operation of the vehicle, and operates while being lubricated by this lubricating oil. However, since the oil pump is stopped when the vehicle is towed, the lubricating oil is not supplied by the oil pump. In this case, the lubricating oil accumulated in the transmission is sprung up by the gear in the transmission that rotates with the rotation of the wheel when the vehicle is towed, so that the outer portion of the ring gear is lubricated. Although it is easy to supply oil, the splashed lubricating oil is difficult to reach the outer part of the ring gear, so it is difficult to supply it to the inner part of the ring gear. In this case, it is difficult to supply the lubricating oil to the planetary gear side, and the supply of the lubricating oil may be insufficient.

  For this reason, some conventional planetary gear mechanism lubrication structures supply lubricant more reliably even when the oil pump is stopped. For example, in the lubricating device for a vehicle transmission described in Patent Document 1, an oil reservoir that accumulates lubricating oil supplied from an inner diameter side to a sun gear, and oil in the oil reservoir by centrifugal force based on rotation of the sun gear is transmitted to a planetary gear. An oil passage leading to the lubricated part is formed. Thereby, even when the oil pump is stopped, if the sun gear is rotating, the oil in the oil reservoir is guided to the lubricated portion of the planetary gear through the oil passage formed in the sun gear by centrifugal force. Accordingly, the planetary gear can be lubricated even when the oil pump is stopped, such as when the vehicle is being towed.

  Further, in a vehicle transmission, since the lubricating oil accumulated in the transmission as described above is sprung up by the gear of the transmission when the vehicle is running, the conventional planetary gear mechanism lubrication structure There are some which are actively lubricated using the splashed lubricating oil. For example, in the lubrication structure of a planetary gear device described in Patent Document 2, an oil path capable of supplying lubricating oil is provided between a support pin and a planetary gear on a support pin serving as a rotation shaft of a planetary gear. The planetary carrier provided integrally is provided with an introduction oil passage capable of guiding the lubricating oil to the oil passage of the support pin.

  Further, the introduction oil passage is bent in an S-shape, and when the lubricating oil flowing from the inner diameter side to the outer diameter side flows into the introduction oil passage by centrifugal force when the planetary carrier rotates, it does not flow out to the outer diameter side. It is formed as follows. Furthermore, since this introduction oil path is bent in an S-shape, when the planetary carrier stops rotating, it is sprung up by another gear in the transmission, and the lubricating oil is introduced from the upper side to the lower side by gravity. It is formed so as not to flow downward when it flows into the oil passage. Accordingly, the lubricating oil can be guided from the introduction oil passage to the oil passage of the support pin regardless of the rotation state of the planetary carrier, and the support pin and the planetary gear can be lubricated.

JP 2004-211801 A JP 2004-270736 A

  Here, in the planetary gear mechanism, lubricating oil is supplied from an oil pump into a rotary shaft that is rotatably provided integrally with a carrier that rotatably supports the planetary gear, and the rotary shaft rotates. Some are provided so that the lubricating oil supplied from the oil pump can be supplied to the planetary gear by the centrifugal force. In the case of such a planetary gear mechanism, even if an oil reservoir or an oil passage is provided in the sun gear as in the lubricating device for a vehicle transmission described in Patent Document 1, the lubricating oil supplied by the oil pump flows into the sun gear. Therefore, when the rotating shaft stops, centrifugal force does not act on the lubricating oil, and the lubricating oil is difficult to be supplied in the direction of the planetary gear.

  Further, even in the planetary gear mechanism in which the lubricating oil is supplied from the oil pump into the rotating shaft, the lubricating oil is supplied in the direction of the planetary gear by the centrifugal force when the rotating shaft rotates, and the transmission device even when the rotation stops. Lubricating oil is supplied to the planetary gear mechanism by the lubricating oil splashed up by other gears. However, unlike the case where these lubricating oils are supplied by an oil pump, the amount supplied by centrifugal force or the amount of splashed oil depending on the rotational speed of the rotating shaft, the state of the lubricating oil in the transmission, etc. The direction of the lubricating oil scattered by centrifugal force and splashing changes every moment.

  For this reason, as in the planetary gear device lubrication structure described in Patent Document 2, the introduction oil passage is provided in the planetary carrier, and the lubricating oil scattered around by the centrifugal force during the rotation of the rotating shaft to which the oil is supplied When the lubricating oil splashed up by the gear in the transmission is received by the introduction oil passage, further contrivance is required to stabilize the amount received by the introduction oil passage.

  The present invention has been made in view of the above, and an object of the present invention is to provide a planetary gear mechanism lubrication structure capable of performing stable lubrication regardless of the rotational state.

  In order to solve the above-mentioned problems and achieve the object, a lubricating structure of a planetary gear mechanism according to the present invention is connected to a rotating part provided to be rotatable about a rotation center axis, and to the rotating part, and A lubricating member provided integrally with the rotating portion so as to be rotatable and having a lubricating oil passage for supplying lubricating oil to the lubricating portion; and an opening through which the lubricating oil can enter. The lubricating oil that has entered from the opening is provided so as to be able to be accumulated, and the accumulated lubricating oil can be flowed to the lubricating oil passage, and is connected to the rotating part and integrated with the rotating part. And is provided so as to be rotatable about a rotation axis passing through the lubrication member, and the opening is located on the side where the opening is located with respect to the center of rotation. On the opposite side Characterized in that it and a catch tank having a quantity difference.

  In this invention, it has the catch tank which can store the lubricating oil which enters from an opening part, and this catch tank is provided so that rotation is possible, and it is a weight by the opening part side and the other side. Have a difference. For this reason, at the time of rotation of the rotating part, the catch tank that can rotate together with the rotating part is rotated by centrifugal force so that the heavy side is located outward in the radial direction of rotation. In addition, when the rotating unit is stopped, the catch tank also stops rotating, so that the heavy weight side is rotated downward. As described above, the catch tank rotates in different states depending on the rotation state of the rotating portion due to the weight difference between the opening portion side and the opposite side.

  Further, since the lubricating oil for lubricating the planetary gear mechanism has a different lubrication path depending on the rotation state of the rotating part, a lubrication path corresponding to the rotating state of the rotating part and a catch tank corresponding to the rotating state of the rotating part By combining with the rotation state, the lubricating oil can be stored in the catch tank regardless of whether or not the rotating portion is rotating. Moreover, since this catch tank can flow the accumulated lubricating oil to the lubricating oil path formed in the lubricating member, the rotation of the catch tank is stopped even when the rotating part is rotating. Even in such a case, the lubricating oil can be stored in the catch tank, and the stored lubricating oil can be supplied to the desired lubricating portion from the lubricating oil path by flowing into the lubricating oil path. As a result, stable lubrication can be performed regardless of the rotation state.

  Further, the lubricating structure of the planetary gear mechanism according to the present invention is the lubricating structure of the planetary gear mechanism, wherein the catch tank has a side opposite to the side where the opening is located from the center of rotation, than the side of the opening. Is also heavy.

  In this invention, since the catch tank is heavier on the opposite side to the opening side than the center of rotation than the opening side, when the rotating part rotates, the catch tank is on the side where the opening is located by centrifugal force. The opposite side rotates in a direction located outward in the radial direction around the rotation center axis. For this reason, at the time of rotation of a rotation part, an opening part will be in the state which faced inward in the radial direction centering on a rotation center axis. Thereby, the lubricating oil which goes outside in the radial direction by the centrifugal force from the inside of the catch tank in the radial direction during rotation of the rotary part can be received at the opening. Further, since the catch tank also rotates when the rotating portion rotates, centrifugal force acts on the lubricating oil that has entered the catch tank by being received at the opening. For this reason, this lubricating oil moves outward in the radial direction around the rotation center axis, and moves to the opposite side of the side where the opening is located. Thereby, lubricating oil accumulates in a catch tank.

  In addition, when the rotation of the rotating part is stopped, centrifugal force does not act on the catch tank, so the opposite side of the catch tank to the side where the opening that is heavier than the opening is located is positioned below due to gravity. Rotate in the direction. For this reason, when the rotation of the rotating part is stopped, the opening part is directed upward. As a result, lubricating oil that scatters around the catch tank and falls by gravity can be received at the opening. If lubricating oil enters the catch tank while the catch tank is stopped, the lubricating oil moves downward in the catch tank, that is, on the side opposite to the side where the opening is located. Accumulate inside. Therefore, it is possible to receive the lubricating oil in the catch tank more reliably regardless of the rotation state, and the lubricating oil can be stored in the catch tank. As a result, it is possible to perform the lubrication more stably regardless of the rotation state.

  The planetary gear mechanism lubrication structure according to the present invention is the planetary gear mechanism lubrication structure, wherein the catch tank has a weight on a side opposite to the side where the opening is located from the center of rotation. It is characterized by being.

  In this invention, since the weight is provided on the catch tank on the side opposite to the side where the opening is located, the side where the opening is located and the side opposite to the side where the opening is located from the center of rotation, A weight difference can be provided more reliably. As a result, when the rotating part rotates, the opening can be directed inward in the radial direction around the rotation center axis, and when the rotation of the rotating part stops, the opening can be directed upward. Therefore, it is possible to receive the lubricating oil in the catch tank more reliably regardless of the rotation state, and the lubricating oil can be stored in the catch tank. As a result, it is possible to perform the lubrication more stably regardless of the rotation state.

  The lubrication structure of the planetary gear mechanism according to the present invention has an effect that the lubrication can be stably performed regardless of the rotation state.

  Embodiments of a lubricating structure for a planetary gear mechanism according to the present invention will be described below in detail with reference to the drawings. Note that the present invention is not limited to the embodiments. In addition, constituent elements in the following embodiments include those that can be easily replaced by those skilled in the art or those that are substantially the same.

  FIG. 1 is a schematic diagram of a vehicle including a planetary gear mechanism lubrication structure according to an embodiment. In the following description, the radial direction is the center of rotation that is the axis that is the center when the input shaft 16 of the drive device 15 described below rotates, unless a reference axis or the like is specifically described. The direction orthogonal to the axis 65 is referred to, and the circumferential direction similarly refers to the circumferential direction around the rotation center axis 65. A vehicle 1 shown in the figure includes an engine 3 that is an internal combustion engine and a motor generator 5 that is driven by electricity. The vehicle 1 is a so-called hybrid vehicle in which the engine 3 and the motor generator 5 are used together or selected and used as a power source during traveling. Among these, the motor generator 5 constitutes the drive device 15 together with the power split and integration mechanism 20, the speed reduction mechanism 50, and the differential device 55, and the vehicle 1 connects the engine 3 and the motor generator 5 to the vehicle 1. The vehicle travels by cooperative control by an ECU (Electronic Control Unit) 10 that controls each part.

  The motor generator 5 has a function as an electric motor that converts supplied electric power into mechanical power and a function as a generator that converts input mechanical power into electric power. The first motor generator Two motor generators 5, 6 and a second motor generator 8 are provided. Among these, the 1st motor generator 6 is mainly used as a generator, and the 2nd motor generator 8 is mainly used as an electric motor.

  Further, the drive device 15 has a power for dividing the mechanical power output from the engine 3 as a power transmission mechanism when the mechanical power output from the engine 3 and the motor generator 5 is transmitted to the drive wheels 62 of the vehicle 1. The division / integration mechanism 20, the reduction mechanism 50 that decelerates the rotation transmitted from the power division / integration mechanism 20 and increases the torque, and the mechanical power transmitted from the reduction mechanism 50 is distributed to the left and right drive wheels 62 and output. A differential device 55 is provided.

  Among these, the power split and integration mechanism 20 is constituted by two single pinion planetary gear mechanisms. Specifically, the power split and integration mechanism 20 is a power split planetary gear that can split mechanical power output from the engine 3 into mechanical power that drives the first motor generator 6 and mechanical power that drives the speed reduction mechanism 50. 21 and a reduction planetary gear 41 capable of transmitting the mechanical power output from the second motor generator 8 to the reduction mechanism 50 by reducing the rotational speed and increasing the torque.

  Of the power split planetary gear 21 and the reduction planetary gear 41, the power split planetary gear 21 includes a sun gear 22 and a ring gear 23 arranged coaxially with each other, and a plurality of planetary gears interposed between these gears. 24 and a planetary carrier 25 that supports the planetary gear 24 so as to be capable of rotating and revolving around the rotation center shaft 65. Similarly, the reduction planetary gear 41 includes a sun gear 42 and a ring gear 43 that are arranged coaxially with each other, a plurality of planetary gears 44 interposed between these gears, and a planetary carrier that supports the planetary gear 44 so as to be capable of rotating. 45.

  The power split planetary gear 21 and the reduction planetary gear 41 provided in this way are arranged concentrically, and the ring gear 23 of the power split planetary gear 21 and the ring gear 43 of the reduction planetary gear 41 are integrally coupled. . A counter drive gear 48 that drives a counter shaft 53 of the speed reduction mechanism 50 is provided on the outer peripheral side of the integrally coupled ring gears 23 and 43.

  The input shaft 16 of the drive device 15 provided as a rotation shaft when the output of the engine 3 is input to the drive device 15 is connected to the planetary carrier 25 of the power split planetary gear 21 so as to be integrally rotatable. As a result, the power split planetary gear 21 can divide the output of the engine 3 into mechanical power transmitted from the planetary gear 24 supported by the planetary carrier 25 to the sun gear 22 and mechanical power transmitted to the ring gear 23. It has become.

  The first motor generator 6 is connected to the power split and integration mechanism 20, the drive shaft 7 of the first motor generator 6 is formed in a hollow shape coaxial with the input shaft 16 of the drive device 15, and the power The split planetary gear 21 is connected to the sun gear 22 so as to be integrally rotatable. Accordingly, the mechanical power input from the engine 3 to the power split planetary gear 21 can be transmitted to the first motor generator 6 via the planetary carrier 25, the planetary gear 24, and the sun gear 22, and the first motor generator 6 can be generated by the mechanical power transmitted from the engine 3.

  On the other hand, the planetary carrier 45 of the reduction planetary gear 41 is fixed to the housing of the drive device 15, and the sun gear 42 of the reduction planetary gear 41 is coupled to the drive shaft 9 of the second motor generator 8. Further, since the sun gear 42 is provided so that rotation can be transmitted to the ring gear 43 via the planetary gear 44 supported by the planetary carrier 45, the reduction planetary gear 41 is provided with mechanical power output from the second motor generator 8. Can be transmitted to the ring gear 43 via the sun gear 42 and the planetary gear 44. At this time, the reduction planetary gear 41 can reduce the rotational speed of the mechanical power output from the second motor generator 8, increase the torque, and transmit it to the ring gear 43.

  Since this ring gear 43 is integrally coupled with the ring gear 23 of the power split planetary gear 21, the power split integration mechanism 20 is a machine that is transmitted from the second motor generator 8 to the ring gear 43 of the reduction planetary gear 41. The mechanical power transmitted from the engine 3 to the ring gear 23 of the power split planetary gear 21 can be integrated and transmitted from the counter drive gear 48 to the speed reduction mechanism 50.

  Further, the speed reduction mechanism 50 is coupled to the counter driven gear 51 that meshes with the counter drive gear 48 of the power split and integration mechanism 20, the counter shaft 53 coupled to the counter driven gear 51, and the counter shaft 53. And a final drive gear 54 that meshes with a ring gear 56 of Therefore, the speed reduction mechanism 50 can transmit the mechanical power transmitted from the ring gears 23 and 43 of the power split and integration mechanism 20 to the ring gear 56 of the differential device 55 by reducing the rotational speed and increasing the torque. It has become.

  The differential device 55 includes a ring gear 56 and a differential case 57 that is fixed to the ring gear 56 and rotates integrally. Also, in the differential case 57, a pair of left and right side gears 58 respectively coupled to the left and right drive shafts 61 of the vehicle 1 and two differential pinions 59 that engage with the two side gears 58 at right angles are provided. It has been. Further, the left and right drive shafts 61 are respectively coupled to the side gears 58, and the drive shafts 61 are coupled to the left and right drive wheels 62 of the vehicle 1, respectively.

  FIG. 2 is a detailed view of the power split planetary gear shown in FIG. On the input shaft 16 to which the planetary carrier 25 included in the power split planetary gear 21 is connected, an input shaft oil path 17 is formed which is an oil path through which lubricating oil that lubricates each part of the drive device 15 such as the power split planetary gear 21 is formed. Has been. The input shaft oil passage 17 is formed along the axial direction of the input shaft 16. Furthermore, a plurality of radial oil passages 18 communicating with the input shaft oil passage 17 are formed in the input shaft 16. The radial oil passage 18 is formed in the radial direction of the input shaft 16, one end communicating with the input shaft oil passage 17, and the other end opening on the outer peripheral surface of the input shaft 16. That is, the radial oil passage 18 communicates the input shaft oil passage 17 and the outside of the input shaft 16. Further, the input shaft oil passage 17 is provided so as to be able to supply lubricating oil directly or indirectly by being pumped by an oil pump (not shown).

  The planetary carrier 25 included in the power split planetary gear 21 supports the planetary gear 24 so as to be capable of rotating and revolving. Specifically, the planetary carrier 25 is connected to the input shaft 16. When the input shaft 16 is rotated, the input shaft 16 can be rotated together with the input shaft 16 about a rotation center shaft 65 that is a shaft that becomes a center when the input shaft 16 rotates. In other words, the planetary carrier 25 is provided as a rotating part provided to be rotatable around the rotation center shaft 65. The planetary carrier 25 provided in this way is provided on both sides of the planetary gear 24 in the axial direction when the planetary gear 24 rotates and revolves, and the planetary carriers 25 located on both sides of the planetary gear 24 are The planetary carrier 25 is connected by a connecting portion 26. The connecting portions 26 are provided at a plurality of locations in the circumferential direction around the rotation center shaft 65.

  The planetary carrier 25 provided in this way supports a planetary shaft 30 that supports the planetary gear 24 so as to be capable of rotating. This planetary shaft 30 is formed in a round bar shape, and both ends in the axial direction of the round bar shaft are connected by being caulked to planetary carriers 25 provided on both sides of the planetary gear 24. Thereby, the planetary shaft 30 is provided so as to be rotatable integrally with the planetary carrier 25 when the planetary carrier 25 rotates. In other words, the planetary shaft 30 can revolve around the rotation center shaft 65 by rotating integrally with the planetary carrier 25 when the planetary carrier 25 rotates.

  The planetary gear 24 is formed with a hole larger than the diameter of the planetary shaft 30, and the planetary shaft 30 supports the planetary gear 24 while passing through the hole of the planetary gear 24. At this time, a needle bearing 35 is provided between the planetary shaft 30 and the planetary gear 24. The needle bearing 35 has a plurality of needles 36 that are shorter than half the width of the planetary gear 24 and that are oriented in the same direction as the planetary shaft 30 in two rows. Spacers 37 formed in a ring shape are provided between the rows of the needles 36 arranged in two rows in this way. The combined length of the spacer 37 and the two rows of needles 36 of the needle bearing 35 is approximately the same as the width of the planetary gear 24. In addition, washers 38 are disposed on both ends of the needle bearing 35 or on both sides of the planetary gear 24.

  The needle bearing 35 is provided between the planetary gear 24 and the planetary shaft 30 as described above. However, when the planetary gear 24 rotates, the planetary gear 24 is relative to the planetary shaft 30. Rotate. For this reason, a portion between the planetary gear 24 and the planetary shaft 30 provided with the needle bearing 35 is a lubrication portion that supplies and lubricates the lubricating oil when the planetary gear 24 rotates.

  Further, the planetary shaft 30 is formed with a lubricating oil passage 31 capable of supplying lubricating oil to a lubricating portion between the planetary shaft 30 and the planetary gear 24. Specifically, the lubricating oil passage 31 is a planetary shaft. Lubricating oil can be supplied to a needle bearing 35 provided between 30 and the planetary gear 24. Thus, the planetary shaft 30 is provided as a lubricating member in which the lubricating oil passage 31 for supplying lubricating oil to the lubricating portion is formed.

  The lubricating oil passage 31 formed in the planetary shaft 30 includes an introduction oil passage 32 through which the lubricating oil is introduced and a supply oil passage 33 that supplies the lubricating oil to the needle bearing 35. Among these, the introduction oil passage 32 is formed along the axial direction of the planetary shaft 30, and is formed so as to penetrate the planetary shaft 30 in the axial direction. That is, both ends of the introduction oil passage 32 are open at both ends of the planetary shaft 30.

  The supply oil passage 33 is formed as a hole orthogonal to the axial direction of the planetary shaft 30. The supply oil passage 33 passes through the planetary shaft 30 and opens to the outer peripheral surface of the planetary shaft 30, and also passes through the introduction oil passage 32 formed in the planetary shaft 30. In other words, the supply oil passage 33 communicates with the introduction oil passage 32 and plays a role of communicating the introduction oil passage 32 and the outside of the planetary shaft 30. The supply oil passage 33 formed in this way is formed near the center in the length direction of the planetary shaft 30 and opens near the spacer 37 of the needle bearing 35 located between the planetary shaft 30 and the planetary gear 24. doing. In addition, it is preferable that the formation direction of the supply oil passage 33 penetrating the planetary shaft 30 is a direction along the radial direction of the input shaft 16 and penetrates in this direction.

  The planetary carrier 25 of the power split planetary gear 21 has a planetary carrier 25 on the side closer to the radial oil passage 18 formed on the input shaft 16 of the planetary carriers 25 formed on both sides of the planetary gear 24. A catch tank 70 capable of storing lubricating oil is disposed on the side.

  FIG. 3 is an AA arrow view of FIG. FIG. 4 is a perspective view of the catch tank shown in FIG. The catch tanks 70 are disposed in the planetary carrier 25 in the vicinity of the position where the planetary shaft 30 is provided, and the number of the catch tanks 70 is the same as the number of the planetary gears 24. That is, since the power split planetary gear 21 that is a planetary gear mechanism having a planetary gear mechanism lubrication structure according to the embodiment is provided with three planetary gears 24, three catch tanks 70 are also provided. As described above, the catch tanks 70 provided in the same number as the number of the planetary gears 24 are formed in a substantially semicircular shape when viewed in the axial direction of the planetary shaft 30. The part formed in is a front wall portion 71 formed in a substantially semicircular plate shape. The front wall 71 is connected to a side wall 72 having a predetermined width in the axial direction of the planetary shaft 30 along a curved portion that is the shape of the front wall 71.

  As described above, the side wall portion 72 connected to the front wall portion 71 is located near the center of the full length of the semicircle, that is, opposite to the side where the straight portion is located in the substantially semicircle having the shape of the front wall portion 71. A support member 75 extending in the direction opposite to the side where the front wall portion 71 is located is connected to the vicinity of the portion that protrudes most in the direction. Furthermore, the end of the support member 75 located on the opposite side of the end connected to the side wall 72 is substantially rectangular when viewed in the axial direction of the planetary shaft 30. A bearing portion 76 formed in a plate shape is connected.

  When the catch tank 70 is viewed in the axial direction of the planetary shaft 30, the bearing portion 76 is connected to the support member 75 in a state of protruding to the side where the straight portion of the front wall portion 71 is located. Further, both the bearing portion 76 and the front wall portion 71 are formed with holes having substantially the same size. Among these holes, the hole formed in the front wall portion 71 is a front wall portion side hole portion 77, and the hole formed in the bearing portion 76 is a bearing portion side hole portion 78. The front wall portion side hole portion 77 and the bearing portion side hole portion 78 are formed so that the positions when the catch tank 70 is viewed in the axial direction of the planetary shaft 30 are substantially the same.

  Further, the catch tank 70 is provided with a weight 85 in the vicinity of a portion of the side wall portion 72 to which the support member 75 is connected. The weight 85 is formed in a columnar shape having a substantially semicircular bottom surface. The columnar axial direction is parallel to the axial direction of the planetary shaft 30 and the semicircular shape of the front wall 71 is formed. It is connected to the side wall portion 72 so as to protrude outward in the radial direction. Since the catch tank 70 is provided with the weight 85 as described above, the weight 85 is provided with a virtual line passing through the center of the front wall portion side hole 77 and parallel to the straight portion of the front wall portion 71 as a boundary. When the weight is compared between the side where the weight 85 is not provided and the side where the weight 85 is not provided, the side where the weight 85 is provided is heavier than the side where the weight 85 is not provided.

  The catch tank 70 thus provided is a portion of the planetary carrier 25 where the planetary shaft 30 is provided in a state where the support member 75 and the bearing portion 76 enter the introduction oil passage 32 formed in the planetary shaft 30. It is arranged in the vicinity. Specifically, in the state where the support member 75 and the bearing portion 76 enter the introduction oil passage 32, a round bar having a diameter slightly smaller than the diameter of the hole which is the shape of the front wall portion side hole portion 77 or the bearing portion side hole portion 78. When the catch tank shaft 90 formed in the shape passes through the front wall portion side hole 77 and the bearing portion side hole 78, the catch tank 70 is disposed so as to be rotatable about the catch tank shaft 90. ing. As described above, the catch tank shaft 90 passes through the planetary shaft 30 by entering the introduction oil passage 32 formed in the planetary shaft 30 and is provided as a rotation shaft when the catch tank 70 rotates. . For this reason, the catch tank 70 provided so as to be rotatable about the catch tank shaft 90 is connected to the planetary carrier 25 via the planetary shaft 30.

  In addition, the planetary shaft 30 in which the catch tank 70 is disposed in the vicinity by the support member 75 and the bearing portion 76 entering the introduction oil passage 32 is integrated with the planetary carrier 25 when the planetary carrier 25 rotates. And can be rotated. For this reason, the catch tank 70 is also rotatably provided integrally with the planetary carrier 25 when the planetary carrier 25 rotates. That is, like the planetary shaft 30, the catch tank 70 can revolve around the rotation center axis 65 by rotating integrally with the planetary carrier 25 when the planetary carrier 25 rotates.

  Of the both ends of the catch tank shaft 90 thus provided, the end on the side where the catch tank 70 is located projects from the front wall 71 in the opposite direction to the direction in which the planetary shaft 30 is located, and is a projecting portion A catch tank side fixing portion 91 formed in a shape in which the size of the outer shape is larger than the diameter of the front wall portion side hole portion 77 is provided at the end portion.

  Further, of the both ends of the catch tank shaft 90, the end opposite to the side where the catch tank 70 is located projects from the introduction oil passage 32 of the planetary shaft 30 in the direction opposite to the direction where the catch tank 70 is located. A planetary shaft side fixing portion 92 formed in a shape in which the size of the outer shape is larger than the diameter of the introduction oil passage 32 is provided at the end of the portion. Thus, the catch tank 70 and the catch tank shaft 90 are provided so as not to move in the axial direction of the catch tank shaft 90. In addition, among the opening portions at both ends of the introduction oil passage 32 opened at both ends of the planetary shaft 30, the opening portion located on the opposite side of the side where the catch tank 70 is located is closed by the planetary shaft side fixing portion 92. doing.

  Further, the catch tank 70 provided so as not to move in the axial direction has an end portion on the opposite side to the end portion on the side connected to the front wall portion 71 among the both end portions in the width direction of the side wall portion 72. Are arranged in contact with the planetary carrier 25 or the planetary shaft 30. For this reason, the catch tank 70 has a portion formed by a substantially semi-circular straight line portion which is the shape of the front wall portion 71 and both end portions in the length direction of the side wall portion 72, and this portion is the catch tank. The opening 80 allows the lubricating oil to enter the 70. That is, when the catch tank 70 is disposed on the planetary carrier 25, the side wall 72 is in contact with the planetary carrier 25 or the planetary shaft 30, so the front wall 71, the side wall 72, the planetary carrier 25, and the planetary carrier 25 are in contact with each other. A space having a predetermined volume is defined by the reshaft 30. For this reason, the catch tank 70 is provided so as to be able to store the lubricating oil that has entered from the opening 80, and the opening 80 is an opening portion of this space with respect to the outside of the catch tank 70.

  Further, the opening 80 is a radial direction when the catch tank 70 rotates when viewed from the center of the catch tank shaft 90 or the front wall portion side hole 77 when the catch tank 70 rotates. Is formed on the side opposite to the side where the weight 85 is located. That is, the catch tank 70 has a weight 85 on the side opposite to the side where the opening 80 is located from the center of rotation. For this reason, the catch tank 70 is formed with a difference in weight between the side where the opening 80 is located and the side opposite to the side where the opening 80 is located from the center of rotation. Also, the side opposite to the side where the opening 80 is located, that is, the side where the weight 85 is provided is heavier than the opening 80 side. The same number of catch tanks 70 provided as the number of planetary gears 24 are connected to a plurality of provided planetary shafts 30 in this form.

  Further, since the planetary shaft 30 forms a space in the catch tank 70 together with the planetary carrier 25, the lubricating oil passage 31 formed in the planetary shaft 30 is open to the space in the catch tank 70. . Specifically, the lubricating oil passage 31 has an introduction oil passage 32 having both ends opened at both end portions of the planetary shaft 30 and is open to the space inside the catch tank 70. For this reason, the catch tank 70 can flow the lubricating oil accumulated in the catch tank 70 to the introduction oil passage 32 included in the lubricating oil passage 31.

  The lubrication structure of the planetary gear mechanism according to this embodiment is configured as described above, and the operation thereof will be described below. When the vehicle 1 travels, the vehicle 3 travels by generating power by driving the engine 3 and the motor generator 5 that are power sources. Of these, the power generated by the engine 3 is input to the input shaft 16 and the input shaft 16 rotates. Since the input shaft 16 is connected to the planetary carrier 25 of the power split planetary gear 21, when the input shaft 16 rotates, the planetary carrier 25 also rotates together with the input shaft 16. When the planetary carrier 25 rotates in this way, the rotation is transmitted to the ring gear 23 via the planetary gear 24 supported by the planetary carrier 25, and the speed reduction mechanism 50 from the counter drive gear 48 provided on the outer peripheral side of the ring gear 23. Is transmitted to. The rotation transmitted to the speed reduction mechanism 50 is transmitted to the differential device 55 after the rotational speed is reduced by the speed reduction mechanism 50 to increase the torque. The rotation transmitted to the differential device 55 is distributed to the left and right drive shafts 61, transmitted to the drive shaft 61, and transmitted from the drive shaft 61 to the drive wheels 62. Thereby, the vehicle 1 travels.

  The power generated by the engine 3 is transmitted from the planetary gear 24 to the sun gear 22 when the planetary gear 24 of the power split planetary gear 21 rotates or revolves around the rotation center shaft 65, and is transmitted from the sun gear 22 to the first gear. By being transmitted to the drive shaft 7 of the motor generator 6, transmission to the first motor generator 6 is possible. Thus, the first motor generator 6 to which the power generated in the engine 3 is transmitted generates electricity for driving the second motor generator 8 by this power, or is a battery (not shown) mounted on the vehicle 1. To generate electricity to charge.

  Further, when the vehicle 1 is decelerated, the power of the drive wheels 62 accompanying the inertia of the vehicle 1 is transmitted from the differential device 55 to the speed reduction mechanism 50, and is transmitted from the speed reduction mechanism 50 to the ring gear 23 of the power split planetary gear 21. The power transmitted to the ring gear 23 is transmitted to the sun gear 22 via the planetary gear 24 of the power split planetary gear 21 and can be transmitted from the sun gear 22 to the first motor generator 6. Thereby, electric power can be generated by the first motor generator 6, and regenerative braking, which is braking performed while generating electric power by the inertial force during deceleration of the vehicle 1, can be performed.

  The power generated by the second motor generator 8 is transmitted from the drive shaft 9 of the second motor generator 8 to the sun gear 42 of the reduction planetary gear 41, and the sun gear 42 rotates. The rotation of the sun gear 42 is transmitted to the ring gear 43 via the planetary gear 44 of the reduction planetary gear 41, and is transmitted to the reduction mechanism 50 from the counter drive gear 48 provided on the outer peripheral side of the ring gear 43. As a result, as in the case where the power of the engine 3 is transmitted to the speed reduction mechanism 50 via the power split planetary gear 21, power is transmitted from the speed reduction mechanism 50 to the drive shaft 61 via the differential device 55, and further to the drive wheels. By being transmitted to 62, the vehicle 1 travels.

  As described above, both the power generated by the engine 3 and the power generated by the second motor generator 8 can be transmitted to the drive wheels 62, and the power generated by the engine 3 and the vehicle 1 are traveling. This inertia force is transmitted to the first motor generator 6 so that the first motor generator 6 can generate power.

  As described above, when the vehicle 1 travels, the vehicle 1 can travel by generating power by the engine 3 or the second motor generator 8 or by generating power by the first motor generator 6. When the vehicle travels, the engine 3 and the motor generator 5 perform coordinated control by the ECU 10. For this reason, the engine 3 is not always driven when the vehicle 1 travels, but is driven or stopped as necessary. Thereby, the input shaft 16 of the drive device 15 rotates or stops while the vehicle 1 is traveling.

  FIG. 5 is an explanatory diagram showing a state when the planetary carrier is rotating. 6 is a BB arrow view of FIG. Here, the lubrication of the power split planetary gear 21 constituted by the planetary gear mechanism will be described. Lubrication of the power split planetary gear 21, specifically, lubrication of the rotating portion of the planetary gear 24 included in the power split planetary gear 21 is different depending on whether the input shaft 16 is rotating or stopped. First, the case where the input shaft 16 is rotated by the operation of the engine 3 will be described. Since the oil pump for supplying the lubricating oil to the input shaft oil passage 17 of the input shaft 16 also operates during the operation of the engine 3, Lubricating oil is supplied into the input shaft oil passage 17. The lubricating oil supplied into the input shaft oil passage 17 also flows through the radial oil passage 18 communicating with the input shaft oil passage 17. Since the radial oil passage 18 is formed in the radial direction of the input shaft 16, the lubricating oil that has flowed through the radial oil passage 18 is released to the outside of the input shaft 16 due to the centrifugal force generated by the rotation of the input shaft 16. Then, it goes to the outside in the radial direction as it is (arrow F in FIGS. 5 and 6).

  The lubricating oil discharged from the radial oil passage 18 is thus directed outward in the radial direction of the input shaft 16, and in this direction, the catch tank 70 connected to the planetary carrier 25 of the power split planetary gear 21 is used. Is located. The catch tank 70 is connected to the planetary shaft 30 by a catch tank shaft 90. However, when the input shaft 16 rotates, the planetary carrier 25 connected to the input shaft 16 also rotates. The planetary shaft 30 also revolves around the rotation center axis 65.

  Accordingly, the catch tank 70 connected to the planetary shaft 30 also revolves around the rotation center shaft 65, but the catch tank 70 is provided so as to be rotatable around the catch tank shaft 90. Further, the catch tank 70 is provided with a weight 85, and the weight 85 is heavier on the weight 85 side than the opening 80 side with the front wall portion side hole 77 as a boundary. For this reason, when the catch tank 70 revolves around the rotation center shaft 65 and centrifugal force acts on the catch tank 70, the weight 85 side is positioned outward in the radial direction around the rotation center shaft 65. The catch tank 70 rotates around the catch tank shaft 90. When the catch tank 70 rotates in this way, the opening 80 of the catch tank 70 rotates so as to face inward in the radial direction around the rotation center shaft 65.

  During rotation of the input shaft 16, the catch tank 70 is rotated so that the opening 80 faces inward in the radial direction around the rotation center shaft 65, so that the catch tank 70 is discharged from the radial oil passage 18 of the input shaft 16. When the lubricating oil reaches outward in the radial direction and reaches the portion where the catch tank 70 is located, the reached lubricating oil enters the inside of the catch tank 70 through the opening 80.

  Since the catch tank 70 revolves around the rotation center shaft 65, a centrifugal force acts. However, when the lubricating oil enters the catch tank 70, the centrifugal force also acts on the lubricating oil. . For this reason, the lubricating oil that has entered the catch tank 70 moves away from the opening 80 and flows outward in the radial direction around the rotation center shaft 65, that is, toward the weight 85 in the catch tank 70. It accumulates in the tank 70.

  Further, the introduction oil passage 32 formed in the planetary shaft 30 is open to the inside of the catch tank 70. For this reason, when the lubricating oil accumulates in the catch tank 70, the accumulated lubricating oil flows from the catch tank 70 to the introduction oil passage 32. Lubricating oil that has flowed from the catch tank 70 to the introduction oil passage 32 travels along the introduction oil passage 32 and flows to the supply oil passage 33 that communicates with the introduction oil passage 32. Since the supply oil passage 33 penetrates the planetary shaft 30 and the introduction oil passage 32, the supply oil passage 33 extends in two directions from the introduction oil passage 32 toward the outer peripheral surface of the planetary shaft 30 through the introduction oil passage 32. Of the supply oil passages 33, one of the supply oil passages 33 is located more outward than the introduction oil passage 32 in the radial direction around the rotation center shaft 65. When the input shaft 16 is rotating, the planetary carrier 25 is also rotating, and the planetary shaft 30 connected to the planetary carrier 25 is revolving around the rotation center axis 65. For this reason, centrifugal force is also acting on the planetary shaft 30, and centrifugal force is also acting on the lubricating oil flowing through the lubricating oil passage 31 of the planetary shaft 30, so that the lubricating oil flowing in the supply oil passage 33 is Of the supply oil passages 33 formed in two directions from the introduction oil passage 32, the flow mainly flows into the supply oil passage 33 located outward in the radial direction around the rotation center shaft 65.

  Since the supply oil passage 33 is open to the outer peripheral surface of the planetary shaft 30, the lubricating oil that has flowed into the supply oil passage 33 flows out of the planetary shaft 30. The lubricating oil flows out from the supply oil passage 33 in this way, but a needle bearing 35 is provided around the planetary shaft 30. For this reason, the lubricating oil flows to each part of the needle bearing 35 and lubricates each part. Specifically, the lubricating oil flows between the needle 36 and the planetary shaft 30, between the needle 36 and the planetary gear 24, between the end of the needle 36 and the spacer 37, and between the end of the needle 36 and the washer. 38 to lubricate these parts. As described above, when the input shaft 16 is rotated by the operation of the engine 3, the planetary gear 24 and the planetary shaft 30 are separated by the lubricating oil accumulated in the catch tank 70 by centrifugal force. Lubricate the lubrication part between.

  On the other hand, when the engine 3 stops and the rotation of the input shaft 16 stops, the planetary carrier 25 of the power split planetary gear 21 connected to the input shaft 16 also stops rotating. Furthermore, as the engine 3 stops, the oil pump that supplies the lubricating oil to the input shaft oil passage 17 formed in the input shaft 16 also stops. As a result, the lubricating oil is not supplied to the input shaft oil passage 17, and the lubricating oil in the input shaft oil passage 17 and the radial oil passage 18 has a centrifugal force due to the rotation of the input shaft 16 being stopped. Since it does not act, it will not flow out of the input shaft 16.

  When the engine 3 is stopped and the rotation of the input shaft 16 and the planetary carrier 25 is stopped, the lubricating oil does not flow out from the input shaft 16 in this way, so that it is connected to the planetary carrier 25 of the power split planetary gear 21. Although the lubricating oil does not flow into the catch tank 70 from the input shaft 16, the deceleration of the drive device 15 occurs when the vehicle 1 is running by the power of the second motor generator 8 even when the engine 3 is stopped. The planetary gear 41, the speed reduction mechanism 50, and the differential device 55 are operated. For this reason, even when the rotation of the planetary carrier 25 stops as the input shaft 16 stops rotating, the second motor generator 8 generates power or the vehicle 1 travels inertially. Since the ring gear 23 of the power split planetary gear 21 rotates, the planetary gear 24 of the power split planetary gear 21 rotates or revolves when the rotation of the ring gear 23 is transmitted.

  Here, each device included in the drive device 15 is provided in the housing of the drive device 15, and lubrication when these devices are operated supplies lubricating oil to each part by the above oil pump. In addition, the device of the drive device 15 is performed by splashing up the lubricating oil stored in the housing during operation. That is, the lubricating oil splashed up by the operation of the device included in the driving device 15 scatters in the housing of the driving device 15, and lubrication is performed by supplying the scattered lubricating oil to each device.

  Specifically, a part of the differential device 55 among the devices included in the drive device 15 is immersed in the lubricating oil stored in the housing of the drive device 15. Since the differential shaft 55 is connected to the drive shaft 61 to which the drive wheels 62 are connected, the differential device 55 operates regardless of the operating state of the engine 3 and the motor generator 5 when the vehicle 1 is traveling. For this reason, when the vehicle 1 travels, the lubricating oil in the drive device 15 is splashed up by the differential device 55 regardless of the operating state of the power source. As a result, the lubricant oil is supplied to each device included in the drive device 15, and each device is lubricated by the supplied lubricant oil regardless of the operating state of the power source.

  Thus, when the vehicle 1 is in the running state, the lubricating oil is splashed by the differential device 55 and supplied to each device of the drive device 15 regardless of the driving state of the power source. The lubricating oil is also supplied to the power split planetary gear 21 from the outside of the power split planetary gear 21. When the lubricating oil is supplied to the power split planetary gear 21 from the outside, that is, when the lubricant oil is supplied to the power split planetary gear 21 from the outside in the radial direction around the rotation center shaft 65, This lubricating oil also moves toward the catch tank 70 from the outside of the power split planetary gear 21 with respect to the catch tank 70. Thus, a part of the lubricating oil that has reached the portion where the catch tank 70 is disposed from the outside of the power split planetary gear 21 toward the catch tank 70 is directed downward from above by gravity, The part where the catch tank 70 is located is reached (arrow S in FIGS. 2 and 3).

  Here, the catch tank 70 when the rotation of the input shaft 16 is stopped will be described. When the rotation of the input shaft 16 is stopped, the planetary carrier 25 connected to the input shaft 16 also rotates. Stop. For this reason, the revolution of the planetary shaft 30 that revolves around the rotation center shaft 65 with the planetary carrier 25 stops, and the revolution of the catch tank 70 connected to the planetary shaft 30 also stops. Centrifugal force stops working.

  The catch tank 70 is provided so as to be rotatable about the catch tank shaft 90. Further, since the catch tank 70 is provided with the weight 85, the centrifugal force no longer acts on the catch tank 70. In other words, the catch tank 70 rotates around the catch tank shaft 90 so that the weight 85 side is positioned on the lower side. As a result, the catch tank 70 stops with the weight 85 side positioned on the lower side and the opening 80 side facing upward. For this reason, the lubricating oil that has reached the portion where the catch tank 70 is located in the direction from the outside of the power split planetary gear 21 toward the catch tank 70 and from the top to the bottom is passed from the opening 80 to the catch tank 70. Enter inside.

  Since centrifugal force is not acting on the catch tank 70 in a state where the rotation of the input shaft 16 is stopped, when the lubricating oil enters the catch tank 70, the lubricating oil flows downward due to gravity. That is, the lubricating oil that has entered the catch tank 70 flows toward the weight 85 in the catch tank 70 and accumulates in the catch tank 70.

  In addition, since the introduction oil passage 32 formed in the planetary shaft 30 is open to the inside of the catch tank 70, when the lubricating oil accumulates in the catch tank 70 due to gravity in this way, the planetary carrier Similarly to the case where the lubricating oil is accumulated in the catch tank 70 by centrifugal force at the time of rotation 25, the accumulated lubricating oil flows from the catch tank 70 to the introduction oil passage 32.

  Further, when the lubricating oil that has flowed into the introduction oil passage 32 flows into a portion where the supply oil passage 33 is connected to the introduction oil passage 32, the lubricating oil flows from the introduction oil passage 32 to the supply oil passage 33. When the lubricating oil flows into the supply oil passage 33, the lubricating oil flows downward mainly by gravity. For this reason, the lubricating oil is mainly supplied to the supply oil passage 33 located below the introduction oil passage 32 in the two-way supply oil passage 33 formed from the introduction oil passage 32 toward the outer peripheral surface of the planetary shaft 30. Flowing. The lubricating oil that has flowed into the supply oil passage 33 flows out of the planetary shaft 30 and lubricates the needle bearing 35 as in the case where the input shaft 16 is rotating. As described above, when the rotation of the input shaft 16 and the planetary carrier 25 is stopped by stopping the operation of the engine 3, the lubricating oil splashed up by the differential device 55 enters the catch tank 70. The lubricating portion stored in the catch tank 70 lubricates the lubrication portion between the planetary gear 24 and the planetary shaft 30.

  The lubrication structure of the planetary gear mechanism described above has a catch tank 70 that can store lubricating oil entering from the opening 80. The catch tank 70 is provided so as to be rotatable, and the opening 80 is provided. The side and the opposite side are formed with a weight difference. For this reason, when the planetary carrier 25 rotates, the catch tank 70 that can rotate integrally with the planetary carrier 25 is rotated by centrifugal force so that the heavy side is positioned outward in the radial direction of rotation. . Further, when the planetary carrier 25 stops rotating, the catch tank 70 also stops rotating, so that the heavier side is rotated downward. As described above, the catch tank 70 rotates in different states depending on the rotation state of the planetary carrier 25 due to the weight difference between the opening 80 side and the opposite side.

  Further, the lubricating oil for lubricating the power split planetary gear 21 constituted by the planetary gear mechanism has a different lubrication route or lubrication method depending on the rotation state of the planetary carrier 25, so that it depends on the rotation state of the planetary carrier 25. By combining the lubrication path and the rotation state of the catch tank 70 according to the rotation state of the planetary carrier 25, the lubricating oil is accumulated in the catch tank 70 regardless of whether or not the planetary carrier 25 is rotating. be able to. Further, the catch tank 70 can flow the accumulated lubricating oil to the lubricating oil passage 31 formed in the planetary shaft 30, so that the rotation is stopped even when the planetary carrier 25 is rotating. Even in the case where the lubricating oil is being used, the lubricating oil can be stored in the catch tank 70, and the stored lubricating oil can be supplied to the desired lubricating portion from the lubricating oil path 31 by flowing through the lubricating oil path 31. As a result, stable lubrication can be performed regardless of the rotation state.

  Further, by connecting to the planetary carrier 25 in such a manner that the catch tank 70 is rotatably provided and has a weight difference between the opening 80 side and the opposite side. Without supplying another device such as an oil pump that operates according to the rotation state of the input shaft 16 or the planetary carrier 25 by supplying the lubricating oil to a desired lubricating portion regardless of the rotation state, Lubrication can be performed. As a result, it is possible to suppress an increase in cost when the lubrication is stably performed regardless of the rotation state, and it is not necessary to control a new device, thereby suppressing the complicated control. Can do.

  Further, the catch tank 70 is heavier than the opening 80 side on the side opposite to the opening 80 side than the center of rotation of the catch tank 70. As a result, the side opposite to the side where the opening 80 is located rotates in a direction positioned outward in the radial direction around the rotation center shaft 65. For this reason, when the planetary carrier 25 rotates, the opening 80 is directed inward in the radial direction around the rotation center axis 65. As a result, when the planetary carrier 25 rotates, the opening 80 can receive lubricating oil that is directed radially outward from the inside of the catch tank 70 in the rotational radial direction by centrifugal force. Further, since the catch tank 70 also rotates when the planetary carrier 25 rotates, centrifugal force also acts on the lubricating oil that has entered the catch tank 70 by being received by the opening 80. For this reason, this lubricating oil moves outward in the radial direction around the rotation center shaft 65 and moves to the opposite side of the side where the opening 80 is located. As a result, the lubricating oil accumulates in the catch tank 70.

  Further, when the rotation of the planetary carrier 25 is stopped, centrifugal force does not act on the catch tank 70, so that the catch tank 70 is heavier than the opening 80 side, and the opposite side to the side where the opening 80 is located. It rotates in the direction located below due to gravity. For this reason, when the rotation of the planetary carrier 25 is stopped, the opening 80 faces upward. Accordingly, the opening 80 can receive the lubricating oil that scatters around the catch tank 70 due to the operation of the other devices of the driving device 15 and falls by gravity. When lubricating oil enters the catch tank 70 with the catch tank 70 stopped, the lubricating oil moves downward in the catch tank 70 by gravity, that is, on the side opposite to the side where the opening 80 is located. The lubricating oil accumulates in the catch tank 70. Therefore, the lubricating oil can be received by the catch tank 70 more reliably regardless of the rotation state, and the lubricating oil can be stored in the catch tank 70. As a result, it is possible to perform the lubrication more stably regardless of the rotation state.

  Further, since the weight 85 is provided on the catch tank 70 on the side opposite to the side where the opening 80 is located, the side opposite to the side where the opening 80 is located and the side where the opening 80 is located from the center of rotation. Thus, a weight difference can be more reliably provided. Thereby, when the planetary carrier 25 is rotated, the opening 80 can be directed inward in the radial direction around the rotation center axis 65, and when the rotation of the planetary carrier 25 is stopped, the opening 80 is directed upward. Can be directed. Therefore, the lubricating oil can be received by the catch tank 70 more reliably regardless of the rotation state, and the lubricating oil can be stored in the catch tank 70. As a result, it is possible to perform the lubrication more stably regardless of the rotation state.

  The catch tank 70 is formed in a substantially semicircular shape when viewed in the axial direction of the planetary shaft 30, but the catch tank 70 may be formed in a shape other than this. . The catch tank 70 is provided so as to be able to store the lubricating oil that has entered from the opening 80, and can flow the collected lubricating oil to the lubricating oil passage 31 of the planetary shaft 30, and is provided so as to be rotatable. Furthermore, the shape is not limited as long as it is formed with a weight difference between the opening 80 side and the opposite side.

  The catch tank 70 is provided so as to have a weight difference between the opening 80 side and the opposite side by providing a weight 85 on the opposite side of the side where the opening 80 is located. You may make it have a weight difference by providing except providing. For example, the thickness of the members constituting the catch tank 70 may be different from each other by making the plate thickness on the opposite side of the opening 80 side thicker than the opening 80 side. Good. The catch tank 70 only needs to have a weight difference between the opening 80 side and the opposite side, and any method for having a weight difference is not required.

  Further, the catch tank 70 can store lubricating oil by the front wall portion 71, the side wall portion 72, the planetary carrier 25, and the planetary shaft 30 when the side wall portion 72 contacts the planetary carrier 25 or the planetary shaft 30. Although the space is defined, the catch tank 70 may be formed so that the lubricating oil can be stored alone without using the planetary carrier 25 and the planetary shaft 30. If the catch tank 70 is provided so as to be able to store the lubricating oil that has entered from the opening 80 and can flow to the lubricating oil passage 31 of the planetary shaft 30, the catch tank 70 can store the lubricating oil. The form of is not ask | required.

  In the lubricating structure of the planetary gear mechanism according to the embodiment, three planetary gears 24 included in the power split planetary gear 21 are provided, and three catch tanks 70 are provided according to the planetary gear 24. The number of planetary gears 24 and catch tanks 70 may be other than three. Regardless of the number of planetary gears 24, the catch tank 70 is provided so that lubricating oil can be supplied to the lubricating oil passage 31 formed in the planetary shaft 30 that supports the planetary gear 24 so as to be able to rotate. Even when it is provided, the lubricating oil can be stably supplied to the lubricating portion between the planetary gear 24 and the planetary shaft 30.

  Further, in the planetary gear mechanism lubrication structure according to the embodiment, a part of the differential device 55 is immersed in the lubricating oil stored in the housing of the drive device 15, and the lubrication of each device included in the drive device 15 is performed. While the differential device 55 is activated, the differential device 55 splashes up the lubricating oil and supplies the lubricating oil to each part. However, the lubrication of each device may be performed by other means. For example, lubrication may be performed by splashing the lubricating oil with a device other than the differential device 55, and the lubricating oil may be supplied to each device by a method other than the splashing when the device is operated for lubrication. May be.

  In the lubrication structure of the planetary gear mechanism according to the embodiment, the lubrication structure of the power split planetary gear 21 included in the driving device 15 of the hybrid vehicle is described. However, the lubrication structure of the planetary gear mechanism according to the present invention You may apply to planetary gear mechanisms other than the division | segmentation planetary gear 21. FIG. The planetary gear mechanism lubrication structure according to the present invention may be used for any planetary gear mechanism as long as it is a planetary gear mechanism lubrication structure in which the planetary carrier 25 rotates or stops during operation of the planetary gear mechanism.

  As described above, the planetary gear mechanism lubrication structure according to the present invention is useful in the case where the rotating portion of the planetary gear is more reliably lubricated, and in particular, the state in which the rotation of the input shaft stops during traveling of the vehicle. Suitable for existing planetary gear mechanism.

It is the schematic of a vehicle provided with the lubrication structure of the planetary gear mechanism which concerns on an Example. FIG. 2 is a detailed view of the power split planetary gear shown in FIG. 1. It is an AA arrow line view of FIG. It is a perspective view of the catch tank shown in FIG. It is explanatory drawing which shows a state in case the planetary carrier is rotating. It is a BB arrow line view of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Vehicle 3 Engine 5 Motor generator 6 1st motor generator 8 2nd motor generator 15 Drive apparatus 16 Input shaft 20 Power split integration mechanism 21 Power split planetary gear 24 Planetary gear 25 Planetary carrier 30 Planetary shaft 31 Lubricating oil path 35 Needle bearing 41 Reduction planetary gear 50 Reduction mechanism 55 Differential device 61 Drive shaft 62 Drive wheel 65 Rotation center shaft 70 Catch tank 71 Front wall portion 72 Side wall portion 75 Support member 76 Bearing portion 77 Front wall portion side hole portion 78 Bearing portion side hole portion 80 Opening 85 Weight 90 Catch tank shaft 91 Catch tank side fixing part 92 Planetary shaft side fixing part

Claims (3)

A rotating part provided to be rotatable around a rotation center axis;
A lubricating member connected to the rotating part and provided integrally with the rotating part so as to be rotatable and having a lubricating oil passage for supplying lubricating oil to the lubricating part;
Having an opening through which the lubricating oil can enter, provided so as to be able to store the lubricating oil that has entered through the opening, and allowing the stored lubricating oil to flow through the lubricating oil path; and The rotation unit is connected to the rotation unit, and is provided so as to be rotatable integrally with the rotation unit. Further, the rotation unit is provided so as to be rotatable about a rotation axis passing through the lubricating member and from the rotation center. A catch tank having a weight difference between a side where the opening is located and a side opposite to the side where the opening is located;
A planetary gear mechanism lubrication structure comprising:   2. The lubricating structure for a planetary gear mechanism according to claim 1, wherein the catch tank is heavier on the opposite side to the opening side than the center of rotation than the opening side.   The lubricating structure for a planetary gear mechanism according to claim 1 or 2, wherein the catch tank has a weight on a side opposite to a side where the opening is located with respect to a center of rotation.

Images