JP2017215024A - Power transmission device and power output device equipped with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a technology capable of reducing agitation resistance when scraping a lubricant, and ensuring stable lubricating performance.SOLUTION: Chevron ribs 72 and 92, and projecting ribs 73 and 93 are formed in a housing 32 and a case body 34. The inside of a gear case 30 is partitioned by the chevron ribs 72 and 92 into a first area S1 in which a ring gear 54 is disposed, and a second area S2 in which mainly a first idler gear 46 is disposed. In a roller member storing area RS composed of tip end portions 720a and 920a of the chevron ribs 72 and 92, the projecting ribs 73 and 93, and fastening flange portions 32a and 34a, a roller member 10 is stored. The roller member 10 moves in a direction intercepting a communication opening 101 capable of communicating the first area S1 and the second area S2, according to a flow rate of a lubricant scraped up by the ring gear 54. The communication opening 101 is blocked to reduce dynamic oil surface of the lubricant in the first area S1.SELECTED DRAWING: Figure 14

Description

  The present invention relates to a power transmission device and a power output device including the power transmission device.

  Japanese Patent Laid-Open No. 2012-233516 (Patent Document 1) requires lubricating oil stored in the bottom portion of the case to be scraped up by a diff ring gear, and lubricated including the gear other than the diff ring gear. A power transmission device configured to be supplied to each component is described.

  In the power transmission device, the space in the case is partitioned into a differential chamber in which the ring gear is disposed and a gear chamber in which a gear other than the ring gear is disposed, and the differential chamber and the gear chamber are provided between the bottom wall of the case. A rib configured to have an opening communicating with the opening is provided in the case, and a predetermined member that protrudes in a direction that obstructs the flow of the lubricating oil flowing through the opening is provided in the vicinity of the opening.

  With this configuration, when the flow velocity of the lubricating oil flowing from the gear chamber toward the differential chamber exceeds a predetermined value, turbulence can be generated in the lubricating oil flow, and the equivalent orifice of the opening can be reduced. The amount of lubricating oil flowing from the gear chamber into the differential chamber through the opening can be reduced. As a result, the dynamic oil level of the differential chamber is lowered, and the scraping performance by the differential ring gear can be improved.

JP 2012-233516 A

  However, since the power transmission device described in the above publication is configured to generate turbulent flow in the lubricating oil flow, when the diff ring gear scoops up the lubricating oil, the lubricating oil is likely to foam, and the generated foam As a result, the oil level rises and the lubricating oil may flow out of the air breather, and there is still room for improvement in terms of ensuring stable lubricating performance.

  The present invention has been made in view of the above, and an object of the present invention is to provide a technique capable of achieving both reduction of agitation resistance when the lubricating oil is scraped and securing stable lubricating performance. .

  The power transmission device and the power output device including the power transmission device of the present invention employ the following means in order to achieve the above-described object.

  According to the preferable form of the power transmission device according to the present invention, the case member configured to store the lubricating oil at the bottom, and the first power transmission member housed in the case member so as to be able to scoop up the lubricating oil. The first rotating body, the second rotating body, the first area where the first rotating body is disposed, and the second area where the second rotating body is disposed are configured to partition the inside of the case member, and the first area and the second area And a partition member that forms an opening that can communicate with the first rotating body, and a structure that operates in a direction that blocks the opening based on the flow of lubricating oil in the first region that is scraped up as the first rotating body rotates. A power transmission device is provided. And the interruption | blocking member is comprised so that it may act | operate in the direction in which the flow-path cross-sectional area of an opening part becomes small, so that the flow velocity of the lubricating oil in the 1st area | region which flows with rotation of a 1st rotary body becomes high.

  In the present invention, “to form an opening” typically means that an opening is formed between the partition member and the case member by providing the partition member at a predetermined distance from the case member. This embodiment corresponds to this, but preferably includes an embodiment in which an opening is formed in the partition member itself.

  According to the present invention, when the rotational speed of the first rotating body is high and the flow velocity of the flowing lubricating oil is high, the flow of the lubricating oil from the second region to the first region is limited, and the dynamic in the first region is limited. Reduce oil level. As a result, it is possible to reduce the stirring resistance due to the lubricating oil scooping up of the first rotating body. On the other hand, when the rotational speed of the first rotating body is low and the flow velocity of the flowing lubricating oil is low, the lubricating oil is allowed to flow from the second region to the first region, and the dynamic oil level in the first region is ensured. . Thereby, even if the rotation speed of the first rotating body is low, a sufficient amount of lubricating oil can be scraped up, so that the lubricating performance can be improved.

  In addition, since the foaming of the lubricating oil can be suppressed as compared with the conventional configuration in which turbulent flow is positively generated in the lubricating oil flowing from the second region to the first region, the oil level is increased by the generated bubbles. Thus, it is possible to satisfactorily prevent the lubricating oil from flowing out of the air breather, and to ensure stable lubricating performance.

  According to the further form of the power transmission device according to the present invention, the blocking member is configured not to operate when the flow velocity of the lubricating oil is smaller than a predetermined value.

  According to this embodiment, it is possible to prevent the dynamic oil level on the first region side from being unnecessarily reduced.

  According to the further form of the power transmission device which concerns on this invention, a interruption | blocking member is between the 1st area | region side and the said 2nd area | region side which arise with the flow velocity of the lubricating oil in a 1st area | region increasing. It is configured to operate by pressure difference.

  According to this embodiment, it is possible to easily ensure a configuration that operates in a direction in which the flow path cross-sectional area of the opening portion decreases as the flow velocity of the lubricating oil in the first region increases.

  According to the further form of the power transmission device which concerns on this invention, the interruption | blocking member is comprised as a roller member which interrupts | blocks an opening part. The case member has a rolling surface on which the roller member can roll. And the rolling surface has the inclination which moves a roller member in the direction opposite to the direction which interrupts | blocks an opening part.

  According to this embodiment, a configuration in which the blocking member does not operate when the flow velocity of the lubricating oil is smaller than a predetermined value can be realized by a simple configuration in which only the gravitational force acting on the roller member is used.

  According to the further form of the power transmission device according to the present invention, the first region becomes lower in the vertical direction than the second region side when the vehicle on which the power transmission device is mounted is tilted. When the state is reached, the roller member is configured to be movable at an angle that blocks the opening.

  According to this embodiment, when a vehicle equipped with a power transmission device travels on an uphill road and a large amount of lubricating oil is about to flow from the second region side to the first region side, the rolling surface Since the opening can be blocked by the roller member even if the vehicle has an inclination, the dynamic oil level in the first region is quickly lowered when the vehicle equipped with the power transmission device travels on the uphill road. be able to. Thereby, when the vehicle equipped with the power transmission device travels on the uphill road, it is possible to quickly reduce the agitation resistance due to the lubricating oil scooping up of the first rotating body.

  According to the further form of the power transmission device which concerns on this invention, the interruption | blocking member is comprised so that it may be act | operated by the fluid pressure which increases as the flow velocity of the lubricating oil in a 1st area | region becomes high.

  According to this embodiment, it is possible to easily ensure a configuration that operates in a direction in which the flow path cross-sectional area of the opening portion decreases as the flow velocity of the lubricating oil in the first region increases.

  According to the further form of the power transmission device which concerns on this invention, the interruption | blocking member has a valve member. The valve member is configured to block the opening by moving toward the opening. And the valve member is comprised so that an elastic force may act on the direction opposite to the direction which interrupts | blocks an opening part.

  According to this embodiment, a configuration in which the blocking member does not operate when the flow rate of the lubricating oil is smaller than a predetermined value can be realized by a simple configuration in which only the elastic force acting on the roller member is used.

  According to the further form of the power transmission device which concerns on this invention, the interruption | blocking member has a slit which accept | permits the inflow of the lubricating oil from a 2nd area | region to a 1st area | region. And the slit is comprised so that it may have a channel cross-sectional area smaller than the channel cross-sectional area of an opening part.

  According to this embodiment, since the flow of the lubricating oil from the second region side to the first region side is allowed through the slit even in the state where the opening is blocked by the blocking member, the rotation of the first rotating body Even when the number is high and a large amount of lubricating oil is scraped up, it is possible to satisfactorily suppress the shortage of lubricating oil in the first region.

  According to the further form of the power transmission device which concerns on this invention, a slit is comprised so that it may open toward the flow direction of the lubricating oil which flows in into a 1st area | region from a 2nd area | region.

  According to this embodiment, it is possible to satisfactorily suppress the occurrence of turbulent flow in the lubricating oil flowing from the second region side to the first region side. Thereby, foaming of lubricating oil can be suppressed favorably.

  According to the further form of the power transmission device which concerns on this invention, the holding part comprised so that at least one part of the lubricating oil in the 1st area | region scraped up by the 1st rotary body could be hold | maintained is provided. The holding unit is disposed in the second region. Moreover, the 2nd rotary body is comprised so that the lubricating oil hold | maintained at the holding | maintenance part can be scooped up. And it is comprised so that at least one part of the lubricating oil scraped up by the 2nd rotary body may be guide | induced to a holding | maintenance part.

  According to this embodiment, each part of the apparatus can be lubricated by the lubricating oil that the second rotating body scoops up. In addition, since it is the structure which guides at least one part of the lubricating oil scooped up by the 2nd rotary body to a holding | maintenance part, it can suppress that the lubricating oil hold | maintained at the holding | maintenance part is lost. Therefore, it is possible to stably ensure the lubricity by the lubricating oil that the second rotating body scoops up.

  Moreover, since a certain amount of lubricating oil can be stably held by the holding portion, the dynamic oil level in the first region can be reduced. As a result, it is possible to reduce the stirring resistance due to the lubricating oil scooping up of the first rotating body.

  According to a preferred embodiment of the power output apparatus of the present invention, an internal combustion engine, a generator that generates electric power as the internal combustion engine is driven, a motor that is driven by the electric power generated by the generator, and power from the motor And a power transmission device according to the present invention according to any one of the above-described aspects configured to connect the internal combustion engine and the generator and connect the motor and the drive shaft. .

  According to the present invention, since the power transmission device according to any one of the aspects described above is provided, the same effect as the power transmission device according to the present invention, for example, when the lubricating oil is scraped up An effect of achieving both reduction in stirring resistance and ensuring stable lubrication performance can be achieved.

  ADVANTAGE OF THE INVENTION According to this invention, the technique which can aim at coexistence with reduction of the stirring resistance at the time of scooping up lubricating oil and ensuring of the stable lubrication performance can be provided.

It is a block diagram which shows the outline of a structure of the power output device 1 which concerns on embodiment of this invention. It is explanatory drawing which looked at the structure of the power transmission path by the side of the engine 2 among the power transmission devices 20 from the direction corresponding to the AA cross section of FIG. It is explanatory drawing which looked at the structure of the power transmission path by the side of the motor 4 among the power transmission devices 20 from the direction corresponding to the BB cross section of FIG. 4 is a perspective view of a housing 32. FIG. It is the front view which looked at the housing 32 from the axial direction. 4 is a perspective view of a case body 34. FIG. It is the front view which looked at the case main body from the axial direction. It is explanatory drawing which looked at the power transmission device 20 of the state which removed the case main body 34 from the axial direction. 3 is a perspective view of the power transmission device 20 with a case body 34 removed. FIG. It is a principal part enlarged view which expands and shows the C section of FIG. 2 is a perspective view showing an appearance of a roller member 10. FIG. It is sectional drawing which looked at the power transmission device 20 from the direction corresponding to the DD cross section of FIG. It is explanatory drawing which shows the mode of the lubricating oil at the time of the vehicle carrying the motive power output device 1 driving | running | working forward on a flat road at low speed. It is explanatory drawing which shows the mode of the lubricating oil at the time of the vehicle carrying the power output device 1 driving | running | working forward on a flat road at high speed. It is explanatory drawing which shows the mode of the lubricating oil at the time of the vehicle carrying the power output device 1 traveling forward on an uphill road. It is a block diagram which shows the outline of a structure of the power transmission device 220 of a modification. It is a block diagram which shows the outline of a structure of the housing 232 of a modification. It is the enlarged view which looked at the E section of FIG. 17 from the F direction. It is a block diagram which shows the outline of a structure of the case main body 234 of a modification. FIG. 3 is a configuration diagram showing an outline of a configuration of a valve member 210. FIG. 4 is a perspective view showing an appearance of a housing 211. FIG. 3 is a perspective view showing an appearance of a door member 212. FIG. 5 is an explanatory view showing a state where a valve member 210 is assembled to a housing 232. FIG. 6 is an explanatory view showing a state of the valve member 210 assembled to the housing 232. It is explanatory drawing which shows the mode of the lubricating oil at the time of the vehicle carrying the power transmission device 220 driving forward on a flat road at high speed. It is explanatory drawing which shows the state of the valve member 210 at the time of the vehicle carrying the power transmission device 220 driving forward on a flat road at high speed.

  Next, the best mode for carrying out the present invention will be described using examples.

  A power output apparatus 1 equipped with a power transmission device 20 according to an embodiment of the present invention is connected to the power transmission device 20 according to the embodiment of the present invention and the power transmission device 20 as shown in FIG. The engine 2, the motor 4, and the generator 6 are provided. The engine 2 is an example of an implementation configuration corresponding to the “internal combustion engine” in the present invention.

  As shown in FIG. 2, the power transmission device 20 includes a first input shaft 22 connected to the crankshaft CS of the engine 2 via the flywheel FH and a first output connected to the rotating shaft 16 of the generator 6. A shaft 24, a first gear mechanism TM1 for connecting the first input shaft 22 and the first output shaft 24, a second input shaft 26 connected to the rotating shaft 14 of the motor 4, as shown in FIG. A differential device 28 to which WS is connected, a second gear mechanism TM2 for connecting the second input shaft 26 and the differential device 28, and a gear case 30 for housing them are provided.

  In the present embodiment, for the sake of convenience, the upper side in FIG. 8 is defined as “upper” or “upper”, and the lower side in FIG. 8 is defined as “lower” or “lower”. 8 is defined as “right side” or “right”, and the left side of FIG. 8 is defined as “left side” or “left side”.

  As shown in FIG. 2, the first input shaft 22 is rotatably supported by the gear case 30 via a pair of bearings B1. A spline protrusion is formed on the outer peripheral surface of one end side (right side in FIG. 2) of the first input shaft 22, and the flywheel FH is fitted to the spline protrusion.

  Moreover, the 1st output shaft 24 is rotatably supported by the gear case 30 via a pair of bearing B2, as shown in FIG. A shaft center hole is formed at the shaft center on one end side (left side in FIG. 2) of the first output shaft 24, and a spline groove is formed on the inner peripheral surface of the shaft center hole. The rotating shaft 16 of the generator 6 is fitted in

  As shown in FIG. 2, the first gear mechanism TM <b> 1 includes a first input gear 42 that is integrally formed with the first input shaft 22, a first output gear 44 that is integrally formed with the first output shaft 24, The first idler gear 46 that meshes with the input gear 42 and the first output gear 44, and a first idler shaft 47 that is integrally formed with the first idler gear 46, are used to generate rotation of the crankshaft CS. 6 to the rotating shaft 16. The first output gear 44 and the first idler gear 46 are an example of an implementation configuration corresponding to the “second rotating body” in the present invention.

  Further, as shown in FIG. 2, the first output gear 44 is formed with a smaller diameter than the first input gear 42 and the first idler gear 46, whereby the first gear mechanism TM <b> 1 is connected to the crankshaft CS. The rotation speed is increased and transmitted to the rotating shaft 16 of the generator 6. The first idler shaft 47 is rotatably supported by the gear case 30 via a pair of bearings B3.

  As shown in FIG. 3, the second input shaft 26 is rotatably supported by the gear case 30 via a pair of bearings B4. A shaft center hole is formed at the shaft center on one end side (left side in FIG. 3) of the second input shaft 26, and a spline groove is formed on the inner peripheral surface of the shaft center hole. The rotating shaft 14 of the motor 4 is fitted to the spline recess.

  As shown in FIG. 3, the second gear mechanism TM <b> 2 meshes with the second input gear 52 that is integrally formed with the second input shaft 26, the ring gear 54 that is bolted to the differential device 28, and the second input gear 52. The second idler gear 56, a third idler gear 58 that meshes with the ring gear 54, and a second idler shaft 59 on which the second idler gear 56 is fixed and the third idler gear 58 is integrally formed. The rotation of the rotating shaft 14 of the motor 4 is transmitted to the axles WS and WS. The ring gear 54 corresponds to the “first rotating body” in the present invention, and the axle WS is an example of an implementation configuration corresponding to the “drive shaft” in the present invention.

  Further, as shown in FIG. 3, the second idler gear 56 is formed with a larger diameter than the second input gear 52 and the third idler gear 58, and the third idler gear 58 has a smaller diameter than the ring gear 54. Thus, the second gear mechanism TM2 decelerates the rotational speed of the rotating shaft 14 of the motor 4 and transmits it to the axles WS and WS. The second idler shaft 59 is rotatably supported by the gear case 30 via a pair of bearings B5.

  As shown in FIG. 3, the axles WS and WS are spline-fitted to the differential device 28, and the power is distributed and transmitted while absorbing the speed difference (rotational speed difference) generated between the left and right axles WS and WS. Is configured to do.

  As shown in FIGS. 1 to 3, the gear case 30 includes a housing 32 and a case main body 34. By fastening the fastening flange portion 32a (see FIG. 4) of the housing 32 and the fastening flange portion 34a (see FIG. 6) of the case body 34 with a bolt or the like (not shown), the first input shaft 22 and the first output shaft 24 are connected. An internal space for accommodating the first gear mechanism TM1, the second input shaft 26, the differential device 28, and the second gear mechanism TM2 is formed. Lubricating oil is stored in the lower part of the internal space. The gear case 30 is an example of an implementation configuration corresponding to the “case member” in the present invention.

  As shown in FIGS. 4 and 5, the housing 32 has mounting holes 61, 62, 63, 64, 65 and 68. The periphery of the mounting hole 68 is configured as a substantially frustoconical recess 69 for accommodating most of the differential device 28.

  One of a pair of bearings B1, B2, B3, B4, and B5 is attached to the mounting holes 61, 62, 63, 64, 65, and 68. As shown in FIG. 5, the mounting hole 61 is formed at substantially the center of the housing 32, and the mounting holes 62 and 63 are formed in this order from the mounting hole 61 toward the diagonally lower left side of FIG. ing. More specifically, the mounting holes 61, 62, and 63 are substantially along the first virtual connecting line VCL1 (a straight line having a downward slope toward the left side in FIG. 5) that connects the center of the mounting hole 61 and the center of the mounting hole 63. Are arranged as follows.

  Further, as shown in FIG. 5, the mounting hole 64 is formed close to the upper right side of the mounting hole 61 in FIG. 5, and the mounting holes 65 and 68 are obliquely lower right in FIG. 5 from the mounting hole 64. Are formed in this order. The center of the mounting hole 65 is above the second virtual connection line VCL2 (a straight line having a downward slope toward the right side in FIG. 5) that connects the center of the mounting hole 64 and the center of the mounting hole 68. Placed in position.

  Thus, as shown in FIGS. 8 and 9, the housing 32 includes the first input shaft 22, the first idler shaft 47, and the first output shaft 24 (first virtual shaft 24) that constitute the power transmission path on the engine 2 side. And the second input shaft 26, the second idler shaft 59, and the axle WS constituting the power transmission path on the motor 4 side (arranged in the extending direction of the second virtual connecting line VCL2). Are arranged in a substantially inverted V shape when viewed from the axial direction.

  As shown in FIGS. 5 and 8, the housing 32 includes a chevron rib 72, a projecting rib 73, an arc rib 74, a depending rib 76, and a flange rib 78. Is divided into a first region S1 where the ring gear 54 is disposed and a second region S2 where the first idler gear 46 is mainly disposed. A lower region LS is provided between a lateral rib 72c described later of the angle ribs 72 and a fastening flange portion 32a disposed on the lower side (lower side in FIG. 5) of the fastening flange portion 32a of the housing 32. Is configured. The chevron rib 72 is an example of an implementation configuration corresponding to the “partition member” in the present invention.

  The chevron rib 72 is composed of a first oblique rib 72a, a second oblique rib 72b, and a lateral rib 72c that connects the first and second oblique ribs 72a and 72b, and extends in the direction perpendicular to the plane of FIG. It is formed in a substantially A shape when viewed. The chevron rib 72 is configured to have the same height as the fastening flange portion 32a when viewed in the direction perpendicular to the plane of FIG. That is, the upper end surface in the height direction of the chevron rib 72 and the flange surface of the fastening flange portion 32a are formed flush with each other.

  As shown in FIG. 10, the first oblique rib 72 a is disposed at a position where the tip end portion 720 a is separated from the fastening flange portion 32 a disposed on the lower side of the fastening flange portion 32 a of the housing 32 by a predetermined distance. That is, the opening 79 is formed by the tip end portion 720 a and the fastening flange portion 32 a disposed on the lower side of the housing 32. Then, as shown in FIG. 8, the first oblique rib 72a extends in the tangential direction of the ring gear 54 (substantially parallel to the second virtual connection line VCL2) in a state of being close to the outer peripheral surface of the ring gear 54 from the tip portion 720a. Exist.

  As shown in FIGS. 5 and 10, the tip end portion 720 a of the first oblique rib 72 a is formed in an arc shape that swells toward the attachment hole 68 (the right side in FIGS. 5 and 10). The inner peripheral surface (surface opposite to the mounting hole 68) of the tip portion 720a is configured to have substantially the same curvature as the curvature of the outer peripheral surface of the roller member 10 described later.

  As shown in FIG. 5, the second diagonal rib 72 b has one end connected to the first diagonal rib 72 a and the other end connected to the intersection of the left side wall portion and the lower wall portion of the housing 32. As shown in FIG. 8, the second oblique rib 72b is connected to the first oblique rib 72a and is substantially parallel to the first virtual connecting line VCL1 and extends in the tangential direction of the first idler gear 46, and The first idler gear 46 includes a first arc portion 75 b extending along the outer peripheral surface and a second arc portion 75 c extending along the outer peripheral surface of the first output gear 44. The first and second arc portions 75b and 75c are an example of an implementation configuration corresponding to the “holding portion” in the present invention.

  One end of the straight line portion 75a is connected to the first oblique rib 72a and the other end is connected to the first arc portion 75b. The first arc portion 75b is opposite to the connection side with the straight portion 75a. The end portion is connected to the second arc portion 75c. The second arc portion 75c is connected to the intersection between the left wall portion and the lower wall portion of the housing 32 at the end opposite to the connection side with the first arc portion 75b. As shown in FIGS. 4, 5, and 8, a notch 77 that penetrates the second region S <b> 2 and the lower region LS is formed at the bottom of the first arc portion 75 b.

  As shown in FIGS. 4, 5, 8, 9, and 10, the protruding rib 73 is a portion corresponding to a portion directly below the first oblique rib 72a in the fastening flange portion 32a disposed on the lower side of the housing 32. To the first diagonal rib 72a and the lateral rib 72c. The protruding rib 73 is formed in an arc shape that swells to the second oblique rib 72b side (the mounting hole 62 side, the left side in FIG. 5). The inner peripheral surface of the projecting rib 73 (the surface on the side opposite to the second oblique rib 72b) is configured to have substantially the same curvature as the curvature of the outer peripheral surface of the roller member 10 described later.

  Further, the protruding rib 73 is configured to have the same height as the fastening flange portion 32a when viewed in the direction perpendicular to the plane of FIG. That is, the upper end surface in the height direction of the protruding rib 73 and the flange surface of the fastening flange portion 32a are formed flush with each other.

  Here, as shown in FIG. 10, the tip portion 720 a of the first oblique rib 72 a and the protruding rib 73 constitute a substantially oval region (hereinafter referred to as “roller member accommodation region RS”) in the lower region LS. The The inner wall surface 32b of the fastening flange portion 32a that constitutes a part of the roller member housing region RS is formed so as to rise upward from the protruding rib 73 side toward the distal end portion 720a side. The inclination angle of the inner wall surface 32b is such that a roller member 10 described later moves to the tip 720a side (opening 79 side) when a vehicle equipped with the power output device 1 according to the embodiment of the present invention travels uphill. Is set to a size that can be The inner wall surface 32b of the fastening flange portion 32a constituting a part of the roller member accommodation region RS is an example of an implementation configuration corresponding to the “rolling surface” in the present invention. In addition, a long groove 32c extending from the protruding rib 73 side to the tip end portion 720a side is formed on the wall surface of the housing 32 in the roller member accommodation region RS.

  As shown in FIG. 5, the arc rib 74 is arranged so as to partition the attachment hole 61 and the attachment hole 68 at a position between the attachment hole 61 and the straight portion 75 a. That is, as shown in FIG. 8, the arc rib 74 is formed on the first input gear 42 so as to isolate the first input gear 42 and the ring gear 54 at a position between the first input gear 42 and the linear portion 75 a. It extends along the outer peripheral surface.

  Further, as shown in FIGS. 5 and 8, the arc rib 74 is configured such that one end in the extending direction overlaps with the straight portion 75a in the extending direction of the straight portion 75a, as shown in FIG. Thus, the other end in the extending direction is configured to extend to a position in contact with the tangent line VTL at the meshing portion of the ring gear 54 and the third idler gear 58.

  Further, the arc rib 74 is configured to have the same height as the fastening flange portion 32a when viewed in the direction perpendicular to the paper surface of FIG. That is, the upper end surface in the height direction of the arc rib 74 and the flange surface of the fastening flange portion 32a are formed flush with each other.

  As shown in FIG. 5, the hanging ribs 76 are integrally formed in a hanging shape vertically downward from a position directly above the center of the mounting hole 61 in the breather constituting wall portion 32 d constituting the breather chamber.

  Further, the hanging rib 76 is configured to have the same height as the fastening flange portion 32a when viewed in the direction perpendicular to the sheet of FIG. That is, the upper end surface in the height direction of the hanging rib 76 and the flange surface of the fastening flange portion 32a are formed flush with each other.

  As shown in FIG. 8, the collar rib 78 is directed from the substantially vertical central portion of the right side wall portion of the housing 32 toward the meshing portion of the ring gear 54 and the third idler gear 58 along the outer peripheral surface of the ring gear 54. It is extended.

  As shown in FIGS. 6 and 7, the case body 34 has mounting holes 81, 82, 83, 84, at positions corresponding to the mounting holes 61, 62, 63, 64, 65, 68 formed in the housing 32. 85 and 88 are formed. The other of the pair of bearings B1, B2, B3, B4, B5 is attached to the mounting holes 81, 82, 83, 84, 85, 88.

  That is, in the case main body 34, like the housing 32, the first input shaft 22, the first idler shaft 47, and the first output shaft 24 (extending direction of the first virtual connection line VCL 1) constituting the power transmission path on the engine 2 side. And the second input shaft 26, the second idler shaft 59, and the axle WS (arranged in the extending direction of the second virtual connection line VCL2) constituting the power transmission path on the motor 4 side, as viewed from the axial direction. When arranged, it is arranged so as to form a substantially inverted V shape.

  Further, as shown in FIG. 6, the case main body 34 is configured such that a portion where the attachment hole 88 is formed is one step higher than the other portions. That is, the case main body 34 is configured such that the portion of the case main body 34 in which the mounting holes 81, 82, 83, 84, 85 are formed is concave, and the first input gear 42 and the first input gear 42 are formed in the concave portion CA. The idler gear 46, the first output gear 44, the second input gear 52, and the second idler gear 56 are accommodated.

  Further, as shown in FIGS. 6 and 7, the case main body 34 includes a chevron rib 92, a protruding rib 93, an arc rib 94, and a depending rib 96. 34 is partitioned by a chevron rib 92 into a first region S1 in which the ring gear 54 is disposed and a second region S2 in which the first idler gear 46 is mainly disposed. A lower region LS is configured between the chevron rib 92 and the lower wall portion of the case body 34. The chevron rib 92 is an example of an implementation configuration corresponding to the “partition member” in the present invention.

  The chevron rib 92 includes first and second oblique ribs 92a and 92b and a lateral rib 92c formed at positions facing the first and second oblique ribs 72a and 72b and the lateral rib 72c of the chevron rib 72 of the housing 32. It is configured and formed in a substantially A shape when viewed in the direction perpendicular to the plane of FIG. Further, the chevron rib 92 is configured to have the same height as the fastening flange portion 34a when viewed in the direction perpendicular to the paper surface of FIG. That is, the upper end surface in the height direction of the chevron rib 92 and the flange surface of the fastening flange portion 34a are formed flush with each other.

  As shown in FIG. 7, the first oblique rib 92 a is, like the first oblique rib 72 a provided in the housing 32, a fastening flange portion 34 a in which the distal end portion 920 a is disposed below the fastening flange portion 34 a of the case body 34. And a predetermined distance away from each other. That is, the opening 99 is formed by the tip portion 920a and the fastening flange portion 34a disposed on the lower side of the case main body 34. The opening 99 is formed at a position corresponding to the opening 79 on the housing 32 side.

  As shown in FIGS. 6 and 7, the tip end portion 920a of the first oblique rib 92a is formed in an arc shape that swells toward the attachment hole 88, like the tip end portion 720a of the first oblique rib 72a. The inner peripheral surface (surface opposite to the mounting hole 88) of the tip portion 920a is configured to have substantially the same curvature as the curvature of the outer peripheral surface of the roller member 10 described later.

  Further, as shown in FIGS. 6 and 7, the second oblique rib 92b is formed at a position facing each of the straight portion 75a, the first arc portion 75b, and the second arc portion 75c of the second oblique rib 72a. It comprises a straight line portion 95a, a first arc portion 95b, and a second arc portion 95c. The first and second arc portions 95b and 95c are an example of an implementation configuration corresponding to the “holding portion” in the present invention.

  That is, the straight portion 95a extends along the tangential direction of the first idler gear 46, the first arc portion 95b is configured to follow the outer peripheral surface of the first idler gear 46, and the second arc portion 95c is The first output gear 44 is configured along the outer peripheral surface.

  As shown in FIG. 7, a notch 97 that penetrates the second region S2 and the lower region LS is formed at the bottom of the first arc portion 95b. The notch 97 is formed at a position corresponding to the notch 77 and forms a communication hole that communicates with the second region S2 and the lower region LS when the housing 32 and the case body 34 are fastened. To do.

  The protruding rib 93 is formed in a position and shape facing the protruding rib 73 provided on the housing 32. That is, as shown in FIG. 6 and FIG. 7, the protruding rib 93 has a first oblique rib 92 a from a portion corresponding to a position directly below the first oblique rib 92 a in the fastening flange portion 34 a disposed on the lower side of the case body 34. And it protrudes toward the lateral rib 92c. The protruding rib 93 is formed in an arc shape that swells to the second oblique rib 92b side (the mounting hole 82 side, the right side in FIG. 7). The inner peripheral surface of the projecting rib 93 (the surface on the side opposite to the second oblique rib 92b) is configured to have substantially the same curvature as that of the outer peripheral surface of the roller member 10 described later.

  Further, the protruding rib 93 is configured to have the same height as the fastening flange portion 34a when viewed in the direction perpendicular to the paper surface of FIG. That is, the upper end surface in the height direction of the protruding rib 93 and the flange surface of the fastening flange portion 34a are formed flush with each other.

  Here, like the housing 32, the tip portion 920a of the first oblique rib 92a and the protruding rib 93 form a substantially oval roller member accommodation region RS in the lower region LS. The inner wall surface 34b of the fastening flange portion 34a that constitutes a part of the roller member housing region RS is formed so as to rise upward from the protruding rib 93 side toward the distal end portion 920a side. The inclination angle of the inner wall surface 34b is such that a roller member 10 described later moves to the tip 920a side (opening 99 side) when a vehicle equipped with the power output apparatus 1 according to the embodiment of the present invention travels uphill. Is set to a size that allows. The inner wall surface 34b of the fastening flange portion 34a constituting a part of the roller member accommodation region RS is an example of an implementation configuration corresponding to the “rolling surface” in the present invention. In addition, a long groove 34c extending from the protruding rib 93 side to the distal end portion 920a side is formed on the wall surface of the case main body 34 in the roller member accommodation region RS.

  The arc rib 94 is formed at a position facing the arc rib 74 of the housing 32. That is, the arc rib 94 is configured to extend along the outer peripheral surface of the first input gear 42, and one end of the arc rib 94 overlaps with the straight portion 95a in the extending direction of the straight portion 95a. Is configured to do.

  The arc rib 94 is configured to have the same height as the fastening flange portion 34a when viewed in the direction perpendicular to the plane of FIG. That is, the upper end surface in the height direction of the arc rib 94 and the flange surface of the fastening flange portion 34a are formed flush with each other.

  The hanging rib 96 is formed at a position facing the hanging rib 76 of the housing 32. That is, as shown in FIG. 7, the hanging rib 96 is integrally formed in a hanging shape vertically downward from a position directly above the center of the mounting hole 81 in the breather constituting wall portion 34d constituting the breather chamber.

  Further, the hanging rib 96 is configured to have the same height as the fastening flange portion 34a when viewed in the direction perpendicular to the sheet of FIG. That is, the upper end surface in the height direction of the hanging rib 96 and the flange surface of the fastening flange portion 34a are formed flush with each other.

  When the housing 32 and the case main body 34 thus configured are fastened by bolts or the like (not shown), the chevron ribs 72 of the housing 32, the chevron ribs 92 of the case main body 34, the protruding ribs 73 of the housing 32, and the protruding ribs 93 of the case main body 34, The arc rib 74 of the housing 32 and the arc rib 94 of the case body 34, and the hanging rib 76 of the housing 32 and the hanging rib 96 of the case body 34 abut each other.

  As a result, the internal space of the gear case 30 includes the first region S1 in which the differential device 28 (particularly, the ring gear 54) is accommodated, the first input gear 42 that constitutes the power transmission path on the engine 2 side, and the first idler gear. 46 and the second region S2 in which the first output gear 44 is accommodated. In addition, a roller member accommodation region RS in which a roller member 10 described later is accommodated is formed. At this time, the openings 79 and 99 are aligned to form a communication opening 101 that communicates the first region S1 and the lower region LS (specifically, a roller member housing region RS described later) (see FIG. 12). The communication opening 101 is an example of an implementation configuration corresponding to the “opening” in the present invention.

  The second region S2 includes the first input shaft 22, the second inclined ribs 72b and the second inclined ribs 92b, the arc ribs 74 and 94, and the hanging ribs 76 and 96. It is configured as a closed space except for one side (the first input shaft 22 side, the right side in FIG. 8) of the arrangement direction of the 1 idler shaft 47 and the first output shaft 24 (the extending direction of the first virtual connecting line VCL1). Is done. Specifically, the second region S2 has a fallen U shape extending in the direction along the first virtual connection line VCL1 when viewed from the axial direction of each axis.

  Therefore, as shown in FIG. 8, the second region S <b> 2 is in a state of being isolated from the lower region LS configured in the lower portion of the internal space of the gear case 30 by the chevron rib 72 and the chevron rib 92. In addition, 2nd area | region S2 is connected via the communicating hole comprised by the notches 77 and 97 formed in 1st circular arc part 75b, 95b of 2nd diagonal rib 72b, 92b, lower area | region LS, and communicating opening 101. FIG. 8 is communicated with the first region S1 (in FIG. 8, only the angle ribs 72, the oblique ribs 2b, the first arc portions 75b, and the notches 77 are shown on the base).

  As shown in FIG. 11, the roller member 10 includes a main body portion 12 formed in a substantially columnar shape, and a shaft portion 13 provided so as to protrude in the axial direction of the main body portion 12. Two annular slits 12 a are formed in the body portion 12 in parallel in the axial direction. The outer diameter of the main body 12 is configured to be larger than the opening height h of the communication opening 101 as shown in FIG. That is, the outer diameter of the main body 12 is formed to a size that can close the communication opening 101 by the main body 12. The roller member 10 is an example of the implementation structure corresponding to the "blocking member" in this invention.

  As shown in FIG. 12, the outer diameter of the shaft portion 13 is such that the long grooves 32 c and 34 c are engageable with the long groove 32 c formed on the wall surface of the housing 32 and the long groove 34 c formed on the wall surface of the case body 34. It is formed to be slightly smaller than the groove width. When the housing 32 and the case body 34 are fastened, the roller member 10 is engaged with the long grooves 32c and 34c and the ribs projecting in the roller member housing region RS while being guided by the long grooves 32c and 34c. 73 and 93 and tip portions 720a and 920a.

  In a vehicle equipped with the motive power output device 1 configured in this way, a generator motor drive mode in which the motor 4 is driven using the electric power generated by driving the generator 6 by the engine 2, and power generation by the generator 6 is performed. The discharge motor drive mode in which the motor 4 is driven using the power supplied from the secondary battery, and the power generated by driving the generator 6 by the engine 2 without driving the motor 4 is used as the secondary battery. It is operated in a charging mode for charging.

  Next, the movement of the lubricating oil supplied to each part constituting the power transmission device 20 as the vehicle on which the power output device 1 thus configured is mounted travels forward will be described. First, the movement of the lubricating oil when the vehicle travels forward on a flat road will be described, and then the movement of the lubricating oil when the vehicle travels forward on an uphill road will be described. In the present embodiment, when the vehicle equipped with the power output device 1 travels forward, the second input shaft 26 is counterclockwise by the rotating shaft 14 of the motor 4 as shown in FIGS. It was set as the structure rotated around. Further, the first input shaft 22 is configured to be rotated counterclockwise by the crankshaft CS as shown in FIGS.

  When the vehicle equipped with the power output device 1 travels forward on a flat road, the ring gear 54 is rotated counterclockwise to scoop up the lubricating oil. As shown in FIG. 13, most of the lubricating oil scraped up by the ring gear 54 is scattered to the second region S2 side by the arc ribs 74 and 94 and the collar rib 78, and the power transmission path (mainly the engine 2 side) The first input gear 42, the first idler gear 46, the first output gear 44, and the bearings B1, B2, and B3) are lubricated (FIG. 13 shows only the arc rib 74 and the collar rib 78. ).

  Here, the lubricating oil scattered in the second region S2 is temporarily held by the second oblique ribs 72b and 92b as shown in FIG. The lubricating oil held by the second oblique ribs 72b and 92b is scraped up by the first idler gear 46 and the first output gear 44, and again the power transmission path (mainly the first input gear 42, The first idler gear 46, the first output gear 44, and the bearings B1, B2, B3) are used for lubrication (only the second oblique rib 72b is shown in FIG. 13).

  Then, it is scraped up by the first idler gear 46 and the first output gear 44, and the power transmission path on the engine 2 side (mainly, the first input gear 42, the first idler gear 46, the first output gear 44, and the bearing B1, The lubricating oil used for the lubrication of B2 and B3) collides with the arc ribs 74 and 94 and the hanging ribs 76 and 96, thereby causing the straight portions 75a and 95a, the first arc portions 75b and 95b, and the second arc portion 75c. 95c, and again held by the second oblique ribs 72b, 92b (FIG. 13 shows only the straight portion 75a, the arc rib 74, the hanging rib 76, the first arc portion 75b, and the second arc portion 75c. Have been). That is, the lubricating oil held by the second oblique ribs 72b and 92b is circulated in the second region S2. Thereby, it can suppress that a lot of lubricating oil is unnecessarily hold | maintained in 1st area | region S1.

  When the vehicle travels at a low speed, as shown in FIG. 13, the protruding rib 73 in the roller member accommodation region RS is generated by the roller member 10 due to its own weight and the inclination of the inner wall surfaces 32b, 34b of the fastening flange portions 32a, 34a. , 93, the lubricating oil scattered on the second region S2 side passes through the communication holes formed by the notches 77, 97 formed in the first circular arc portions 75b, 95b and communicates with the lower region LS. In order to return to the first region S1 through the opening 101 (FIG. 13 shows only the fastening flange portion 32a, the inner wall surface 32b, the protruding rib 73, the first arc portion 75b, the notch 77, and the opening 79. In the first region S1, a necessary and sufficient amount of lubricating oil can be secured, and good lubricity when the vehicle is traveling at low speed can be secured.

  On the other hand, when the vehicle travels at a high speed, as shown in FIG. 14, the rotational speed of the ring gear 54 becomes high, so that the flow rate of the lubricating oil in the first region S <b> 1 scraped up by the ring gear 54 is low. It is higher than when driving. As a result, the pressure on the first region side becomes smaller than the pressure on the roller member housing region RS side across the communication opening 101, the roller member 10 is sucked toward the first region S <b> 1, and the communication opening 101 is formed by the roller member 10. It is blocked.

  As a result, the flow of the lubricating oil from the second region S2 side to the first region S1 side through the lower region LS and the communication opening 101 from the communication hole formed by the notches 77 and 97 is suppressed, and the first region Since the dynamic oil level of the lubricating oil in S1 is reduced, it is possible to reduce agitation resistance caused by scooping up the lubricating oil in the ring gear 54.

  Here, since the annular slit 12a is formed in the roller member 10, even if the communication opening 101 is blocked by the roller member 10, the magnitude of the pressure change generated on the first region S1 side across the communication opening 101. Therefore, the amount of lubricating oil on the first region S1 side will not be insufficient.

  Since the annular slit 12a is configured to open with respect to the flow of the lubricating oil, the lubricating oil flowing from the communication opening 101 to the first region S1 side through the annular slit 12a is rectified. Therefore, since it is possible to suppress the occurrence of turbulent flow in the lubricating oil in the first region S1, it is possible to satisfactorily suppress the occurrence of foaming in the lubricating oil when the ring gear 54 is scraped up. Thereby, it is possible to satisfactorily suppress the lubricating oil from rising from the air breather (not shown) due to the rising of the oil level due to the generated bubbles.

  Further, when the vehicle changes from high speed to low speed, the rotation speed of the ring gear 54 decreases, and the roller member 10 is caused by its own weight and the inclination of the inner wall surfaces 32b, 34b of the fastening flange portions 32a, 34a. Since the communication opening 101 is opened by moving closer to the protruding ribs 73 and 93 in the accommodation region RS, the second region S2 through the lower region LS and the communication opening 101 from the communication hole formed by the notches 77 and 97 is opened. The flow of the lubricating oil from the side to the first region S1 is allowed, and a sufficient amount of lubricating oil is ensured in the first region S1 in order to ensure good lubricity when the vehicle is traveling at low speed.

  Next, the movement of the lubricating oil when the vehicle travels forward on an uphill road will be described. When the vehicle travels forward on an uphill road, as shown in FIG. 15, the power transmission device 20 is tilted so that the first region S1 is lower than the second region S2. At this time, the roller member 10 moves in the roller member accommodating region RS toward the front end portions 720a and 920a by its own weight, and the communication opening 101 is closed (FIG. 15 shows only the front end portion 720a and the opening 79. Have been).

  Thereby, the flow of the lubricating oil from the second region S2 side to the first region S1 side through the lower region LS and the communication opening 101 from the communication hole formed by the notches 77 and 97 is suppressed, and the first region Since the dynamic oil level of the lubricating oil in S1 is reduced, it is possible to reduce agitation resistance caused by scooping up the lubricating oil in the ring gear 54.

  Since the annular slit 12a is formed in the roller member 10, even when the communication opening 101 is blocked by the roller member 10 as in the case where the vehicle travels at a high speed, the first region S1 is sandwiched by the communication opening 101. Since the amount of lubricating oil corresponding to the magnitude of the pressure change occurring on the side can be introduced from the lower region LS, the amount of lubricating oil on the first region S1 side will not be insufficient. Moreover, since it can suppress that a turbulent flow arises in lubricating oil in 1st area | region S1, it can suppress favorably that foaming arises in lubricating oil at the time of the scraping by the ring gear 54. FIG.

  In the present embodiment, the roller member 10 is operated using the pressure change on the first region S1 side that is generated when the ring gear 54 scoops up the lubricating oil, thereby moving from the second region S2 side to the first region S1 side. Although it was set as the structure which restrict | limits the lubricating oil amount which flows in, it does not restrict to this. For example, as illustrated in the power transmission device 220 of the modified example of FIG. 16, the valve member 210 is operated using the fluid pressure of the lubricating oil that the ring gear 54 scrapes up, thereby causing the first region from the second region S2 side. It is good also as a structure which restrict | limits the amount of lubricating oil which flows in into S1 side.

  The power transmission device 220 of the modified example is the same as the power transmission device 20 according to the embodiment of the present invention except that the configuration for limiting the amount of lubricating oil flowing from the second region S2 side to the first region S1 side is different. It has the configuration of Therefore, among the configurations of the power transmission device 220 according to the modification, the same configurations as those of the power transmission device 20 according to the embodiment of the present invention are denoted by the same reference numerals, and description thereof is omitted.

  As shown in FIG. 17, the housing 232 of the power transmission device 220 according to the modified example is formed in a mountain-shaped partition wall by forming a lower fastening flange portion 232 a of the fastening flange portion 232 a (lower side in FIG. 17) into a mountain shape. 272 is configured. The mountain-shaped partition wall 272 has first and second inclined surface portions 272a and 272b corresponding to the first and second oblique ribs 72a and 72b of the power transmission device 20 according to the embodiment of the present invention. A stepped portion 272a 'is formed on the first inclined surface portion 272a. The mountain-shaped partition wall 272 is an example of an implementation configuration corresponding to the “partition member” in the present invention.

  As shown in FIG. 17, the second inclined surface portion 272b includes a straight portion 275a corresponding to the straight portion 75a, the first arc portion 75b, and the second arc portion 75c of the power transmission device 20 according to the embodiment of the present invention. It has a first arc portion 275b and a second arc portion 275c. The first and second arc portions 275b and 275c are an example of an implementation configuration corresponding to the “holding portion” in the present invention.

  As shown in FIG. 17, the mountain-shaped partition wall 272 is formed with a flow path 273 that penetrates from the first slope portion 272 a to the second slope portion. The flow path 273 has an opening 273a on the first slope portion 272a side and an opening 273b on the second slope portion 272b side. The opening 273a is formed so as to open to the stepped portion 272a ', and the opening 273b is formed at a position near the first arc portion 275b in the straight portion 275a. The opening 273a is an example of an implementation configuration corresponding to the “opening” in the present invention.

  Further, as shown in FIG. 18, a projection 277 is formed on the connection surface 272 a ″ between the stepped portion 272 a ′ and the first inclined surface portion 272 a. The protrusion 277 has a protrusion main body part 277a and an annular protrusion part 277b integrally formed in an annular shape with the protrusion main body part 277a, and the protrusion 277 is a spring SPR of the valve member 210 described later. It is comprised as a latching | locking part which latches.

  As shown in FIG. 19, the case main body 234 of the power transmission device 220 according to the modified example is formed by forming a lower fastening flange portion 234 a of the fastening flange portion 234 a (lower side in FIG. 19) into a mountain shape. A mountain-shaped partition wall 292 corresponding to the mountain-shaped partition wall 272 of 232 is configured. The mountain-shaped partition wall 292 has first and second slope portions 292a and 292b corresponding to the first and second oblique ribs 92a and 92b of the power transmission device 20 according to the embodiment of the present invention. The mountain-shaped partition wall 292 is an example of the implementation structure corresponding to the “partition member” in the present invention.

  As shown in FIG. 19, the second inclined surface portion 292b includes a linear portion 295a, a linear portion 295a corresponding to the linear portion 95a, the first circular arc portion 95b, and the second circular arc portion 95c of the power transmission device 20 according to the embodiment of the present invention. It has a first arc portion 295b and a second arc portion 295c. The first and second arc portions 295b and 295c are an example of an implementation configuration corresponding to the “holding portion” in the present invention.

  As illustrated in FIG. 20, the valve member 210 includes a housing 211, a door member 212, and a spring SPR. As shown in FIG. 21, the housing 211 has two arm portions 211a and a connection portion 211b that connects these arm portions 211a, and is configured in an inverted U shape. Inside the valve member 210, a groove 211 'is formed which continues from one arm portion 211a to the other arm portion 211a via the connecting portion 211b. The valve member 210 is an example of the implementation structure corresponding to the "blocking member" in this invention.

  As shown in FIG. 22, the door member 212 includes a main body 212 a and a flange 212 b that protrudes from the main surface of the main body 212 a. A notch 212a 'is formed in the lower portion of the main body 212a. A pin portion 212c protruding downward is provided on the upper surface of the notch 212a '. The valve member 210 is completed by inserting the door member 212 into the groove 211 ′ of the housing 211 and attaching a spring SPR to the pin portion 212 c of the door member 212 (see FIG. 24). The notch 212a 'is an example of an implementation configuration corresponding to the "opening" in the present invention.

  As shown in FIGS. 23 and 24, the valve member 210 configured in this manner is assembled to the step portion 272a ′ of the first inclined surface portion 272a. At this time, the spring SPR is locked to the protrusion 277 of the stepped portion 272a '. In a state where the valve member 210 is assembled to the stepped portion 272a ′, the door member 212 is urged toward the connection portion 211b side of the housing 211 by the spring force of the spring SPR as shown in FIG. Yes. Thereby, the opening 273a of the flow path 273 is not blocked by the door member 212, and the first area S1 and the second area S2 are in communication with each other via the flow path 273.

  Next, the movement of the lubricating oil in the power transmission device 220 of the modified example configured as described above will be described. While the vehicle equipped with the power transmission device 220 is traveling at a low speed, the spring of the spring SPR of the valve member 210 is swept up by the ring gear 54 and the fluid pressure of the lubricating oil acting on the flange portion 212b of the valve member 210. Since the force is set to be larger, the door member 212 does not block the opening 273a. As a result, a sufficient amount of lubricating oil flows from the second region S2 side through the flow path 273 to the first region S1, so that a necessary and sufficient amount of lubricating oil can be secured in the first region S1. And good lubricity when the vehicle is traveling at low speed can be ensured.

  On the other hand, when the vehicle travels at a high speed, as shown in FIG. 25, the rotational speed of the ring gear 54 becomes high, so that the fluid of the lubricating oil that is scraped up by the ring gear 54 and acts on the flange 212b of the valve member 210. The pressure becomes larger than the spring force of the spring SPR of the valve member 210. As a result, the door member 212 is moved downward in the direction of closing the opening 273a, as shown in FIG.

  As a result, the flow of the lubricating oil from the second region S2 side to the first region S1 side through the flow path 273 is suppressed, and the dynamic oil level of the lubricating oil in the first region S1 is reduced. The agitation resistance caused by scooping up the lubricating oil of the ring gear 54 can be reduced.

  Here, since the notch 212a ′ is formed in the door member 212, the amount of lubricating oil corresponding to the magnitude of the pressure change generated on the first region S1 side across the opening 273a is passed through the flow path 273. Since it can be made to flow into 1 area | region S1, the amount of lubricating oil by the side of 1st area | region S1 is not insufficient.

  Since the notch 212a ′ is configured to open to the flow of the lubricating oil, a turbulent flow is generated in the lubricating oil flowing from the opening 273a to the first region S1 through the notch 212a ′. Since this can be suppressed, foaming of the lubricating oil can be satisfactorily suppressed when the ring gear 54 is scraped up. Thereby, it is possible to satisfactorily suppress the lubricating oil from rising from the air breather (not shown) due to the rising of the oil level due to the generated bubbles.

  In the power transmission devices 20 and 220 of the present embodiment and the modification, the roller member 10 and the door member 212 are provided with the annular slit 12a and the notch 212a ′. However, the annular slit 12a and the notch 212a ′ are not provided. Also good.

  In the power transmission devices 20 and 220 of the present embodiment and the modified example, the reduction gear for a hybrid vehicle is used, but the invention is not limited to this. For example, it may be a stepped transmission, a continuously variable transmission, and a speed increaser for a hybrid vehicle. Further, a reduction gear, a stepped transmission, a continuously variable transmission, and a speed increaser for an automobile that runs only by an engine may be used.

  This embodiment shows an example for carrying out the present invention. Therefore, the present invention is not limited to the configuration of the present embodiment.

1 Power output device (power output device)
2 Engine (Internal combustion engine)
4 Motor (motor)
6 Generator (generator)
10 Roller member (blocking member, roller member)
12 Body 12a Annular slit (slit)
13 Shaft portion 14 Motor rotation shaft 16 Generator rotation shaft 20 Power transmission device (power transmission device)
22 First Input Shaft 24 First Output Shaft 26 Second Input Shaft 28 Differential Device 30 Gear Case (Case Member)
32 housing 32a fastening flange portion 32b inner wall surface 32c long groove 32d breather constituting wall portion 34 case body 34a fastening flange portion 34b inner wall surface 34c long groove 34d breather constituting wall portion 42 first input gear 44 first output gear (second rotating body)
46 First idler gear (second rotating body)
47 1st idler shaft 52 2nd input gear 54 Ring gear (first rotating body)
56 2nd idler gear 58 3rd idler gear 59 2nd idler shaft 61 mounting hole 62 mounting hole 63 mounting hole 64 mounting hole 65 mounting hole 68 mounting hole 69 space 72 chevron rib (partition member)
72a First oblique rib 72b Second oblique rib 72c Lateral rib 73 Projecting rib 74 Arc rib 75a Straight line portion 75b First arc portion (holding portion)
75c Second arc portion (holding portion)
76 Hanging rib 77 Notch 78 庇 Rib 79 Opening 81 Mounting hole 82 Mounting hole 83 Mounting hole 84 Mounting hole 85 Mounting hole 88 Mounting hole 92 Angle rib (partition member)
92a First oblique rib 92b Second oblique rib 92c Lateral rib 93 Protruding rib 94 Arc rib 95a Linear portion 95b First arc portion (holding portion)
95c Second arc portion (holding portion)
96 Hanging rib 97 Notch 99 Opening 101 Communication opening (opening)
210 Valve member (blocking member)
211 Housing 211 'Groove 211a Arm part 211b Connection part 212 Door member 212a Body part 212a' Notch (slit)
212b collar 212c pin 220 power transmission device (power transmission device)
232 Housing 232a Fastening flange portion 234 Case body 234a Fastening flange portion 272 Angle partition wall (partition member)
272a First slope part 272a 'Step part 272a "Connection surface 272b Second slope part 273 Flow path 273a Opening (opening part)
273b Opening 275a Straight part 275b First arc part (holding part)
275c Second arc part (holding part)
277 Projection 277a Projection body 277b Annular projection 292 Angle partition wall (partition member)
292a First slope portion 292b Second slope portion 295a Linear portion 295b First arc portion (holding portion)
295c Second arc part (holding part)
720a Tip 920a Tip CS Crankshaft FH Flywheel TM1 First gear mechanism (first gear mechanism)
TM2 Second gear mechanism (second gear mechanism)
B1 bearing B2 bearing B3 bearing B4 bearing B5 bearing WS axle (drive shaft)
VCL1 first virtual connection line (first virtual connection line)
VCL2 second virtual connection line (second virtual connection line)
VTL Tangent CA Concave portion S1 First region (first region)
S2 Second area (second area)
LS Lower area RS Roller member accommodation area SPR Spring

Claims (11)

A case member configured to store lubricating oil at the bottom,
First and second rotating bodies as power transmission members accommodated in the case member so as to be able to scoop up the lubricating oil;
The interior of the case member is partitioned into a first area where the first rotating body is arranged and a second area where the second rotating body is arranged, and the first area and the second area A partition member forming an opening capable of communicating with the region;
A blocking member configured to operate in a direction to block the opening based on the flow of the lubricating oil in the first region scraped up with the rotation of the first rotating body;
With
The blocking member is configured to operate in a direction in which the flow passage cross-sectional area of the opening portion decreases as the flow velocity of the lubricating oil in the first region that flows with the rotation of the first rotating body increases. Transmission device. The power transmission device according to claim 1, wherein the blocking member is configured not to operate when a flow rate of the lubricating oil is smaller than a predetermined value. 2. The blocking member is configured to be operated by a pressure difference between the first region and the second region that occurs as the flow rate of lubricating oil in the first region increases. 2. The power transmission device according to 2. The blocking member is configured as a roller member that blocks the opening,
The case member has a rolling surface on which the roller member can roll,
The power transmission device according to claim 3, wherein the rolling surface has an inclination to move the roller member in a direction opposite to a direction in which the opening is blocked. The inclination is such that when the vehicle on which the power transmission device is mounted is inclined and the first region is in a state vertically below the second region, the roller member is The power transmission device according to claim 4, wherein the power transmission device is configured at an angle movable in a direction to block the opening. The power transmission device according to claim 1, wherein the blocking member is configured to be operated by a fluid pressure that increases as a flow rate of the lubricating oil in the first region increases. The blocking member has a valve member, and is configured to block the opening by moving the valve member to the opening.
The power transmission device according to claim 6, wherein the valve member is configured such that an elastic force acts in a direction opposite to a direction in which the opening is blocked. The blocking member has a slit that allows inflow of lubricating oil from the second region to the first region;
The power transmission device according to any one of claims 1 to 7, wherein the slit is configured to have a channel cross-sectional area smaller than a channel cross-sectional area of the opening. The power transmission device according to claim 8, wherein the slit is configured to open in a flow direction of the lubricating oil flowing from the second region into the first region. A holding portion configured to hold at least a part of the lubricating oil in the first region scraped up by the first rotating body;
The holding portion constitutes the second region,
The second rotating body is configured to be able to scoop up the lubricating oil held in the holding portion,
The power transmission device according to any one of claims 1 to 9, wherein the power transmission device is configured to guide at least part of the lubricating oil scraped up by the second rotating body to the holding portion. An internal combustion engine;
A generator for generating electricity as the internal combustion engine is driven;
A motor driven by the power generated by the generator;
A drive shaft for outputting power from the motor;
The power transmission device according to any one of claims 1 to 10, wherein the power transmission device is configured to connect the internal combustion engine and the generator and to connect the motor and the drive shaft.
A power output device comprising:

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