WO2023190129A1 - Drive transmission device for vehicle - Google Patents
Drive transmission device for vehicle Download PDFInfo
- Publication number
- WO2023190129A1 WO2023190129A1 PCT/JP2023/011764 JP2023011764W WO2023190129A1 WO 2023190129 A1 WO2023190129 A1 WO 2023190129A1 JP 2023011764 W JP2023011764 W JP 2023011764W WO 2023190129 A1 WO2023190129 A1 WO 2023190129A1
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- WO
- WIPO (PCT)
- Prior art keywords
- oil
- carrier
- scraping
- case
- axial
- Prior art date
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 56
- 238000005461 lubrication Methods 0.000 claims abstract description 26
- 230000007246 mechanism Effects 0.000 claims abstract description 25
- 230000002093 peripheral effect Effects 0.000 claims abstract description 18
- 239000003921 oil Substances 0.000 claims description 263
- 238000007790 scraping Methods 0.000 claims description 82
- 238000004891 communication Methods 0.000 claims description 19
- 239000002199 base oil Substances 0.000 claims description 6
- 238000003756 stirring Methods 0.000 description 8
- 238000003466 welding Methods 0.000 description 6
- 238000013019 agitation Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000001050 lubricating effect Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 238000007654 immersion Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000009751 slip forming Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
Definitions
- the present invention relates to a vehicle drive transmission device equipped with a planetary gear mechanism.
- a vehicle drive transmission device that includes a planetary gear mechanism and a scraping part for scraping up oil in a case.
- Patent Document 1 describes a vehicle drive transmission device including a stirring blade that rotates together with a carrier to scrape up oil in a stirring chamber.
- the vehicle drive transmission device described in Patent Document 1 has a configuration in which the oil in the stirring chamber is scraped up by the stirring blade, and the lower end of the revolution trajectory of the pinion is arranged below the lower end of the stirring blade. Therefore, there was a problem in that the proportion of the pinion immersed in oil tends to increase, and the amount of oil agitation tends to increase.
- a vehicle drive transmission device includes an input shaft that is drivingly connected to a drive source, an output shaft that is drivingly connected to a wheel, and a system that decelerates the rotation of the input shaft and transmits it to the output shaft.
- a vehicle drive transmission device comprising a planetary gear mechanism for deceleration and a case accommodating the planetary gear mechanism, the planetary gear mechanism being connected to the input shaft so as to rotate integrally with the input shaft.
- a scraping part for scraping up is provided, the direction along the rotational axis of the carrier is the axial direction, and the direction along the vertical direction is the vertical direction, and the scraping part is arranged in one direction in the axial direction with respect to the ring gear.
- the lower end of the rotational trajectory of the scraping part is arranged below the lower end of the revolving trajectory of the pinion, and the oil scraped up by the scraping part is directed to areas requiring lubrication in the case.
- An oil supply path is formed to allow the oil to flow.
- the scraping part can scrape up the oil and supply oil to the parts that require lubrication, so the pinion can It is easy to reduce the oil agitation caused by the pinion by reducing the immersion ratio. Therefore, the oil can be appropriately scraped up by the scraping section while minimizing the rotational resistance of the planetary gear mechanism due to stirring of the oil.
- a schematic diagram of a vehicle equipped with a vehicle drive transmission device according to an embodiment of the present invention A cross-sectional view of a vehicle drive transmission device according to a first embodiment Schematic diagram of the side view of the vehicle drive transmission device in Figure 2 An enlarged view of the upper part of the vehicle drive transmission device in FIG. 2 An enlarged view showing the lower part of the vehicle drive transmission device in FIG. 2 A sectional view of a vehicle drive transmission device according to a second embodiment A diagram showing another example of a vehicle equipped with a vehicle drive transmission device according to an embodiment of the present invention.
- a vehicle drive transmission device 10 (hereinafter referred to as a drive transmission device) 10 according to a first embodiment will be described with reference to FIGS. 1 to 5.
- FIG. 1 is a schematic diagram of a vehicle 11 equipped with a drive transmission device 10.
- FIG. 2 is a sectional view of the drive transmission device 10.
- FIG. 3 is a schematic side view of the drive transmission device 10 viewed from the first axial side X1.
- the drive transmission device 10 is mounted on a vehicle 11 that includes a drive source 12 such as a rotating electric machine, a differential gear device 13, and wheels 14, for example.
- the differential gear device 13 distributes the driving force input from the drive source 12 via the drive transmission device 10 to the pair of wheels 14 .
- the term "rotating electric machine” is used as a concept that includes a motor (electric motor), a generator (generator), and, if necessary, a motor/generator that functions as both a motor and a generator.
- the drive transmission device 10 includes an input shaft 15 drivingly connected to a drive source 12, an output shaft 16 drivingly connected to the wheels 14, and a deceleration planet that decelerates the rotation of the input shaft 15 and transmits it to the output shaft 16. It includes a gear mechanism 20 and a case 50 that accommodates the planetary gear mechanism 20.
- the input shaft 15 and the output shaft 16 are arranged coaxially, and the input shaft 15 and the output shaft 16 are arranged side by side in the axial direction X, which will be described later.
- the input shaft 15 is rotatably supported with respect to the case 50 by an input bearing 71.
- the output shaft 16 is rotatably supported with respect to the case 50 by an output bearing 72.
- the input shaft 15 is supported by a pair of input bearings 71.
- the output shaft 16 is supported by a pair of output bearings 72.
- drive connection refers to a state in which two rotating elements are connected so that driving force can be transmitted, and a state in which the two rotating elements are connected so that they rotate integrally, or a state in which the two rotating elements are connected so that they rotate integrally. It is used as a concept that includes a state in which two rotating elements are connected so that driving force can be transmitted via one or more transmission members.
- Such transmission members include various members that transmit rotation at the same speed or at variable speeds, and include, for example, shafts, gear mechanisms, belts, chains, and the like.
- a transmission member may include an engagement device that selectively transmits rotation and driving force, such as a friction engagement device or a meshing engagement device.
- the planetary gear mechanism 20 includes a sun gear 21 connected to rotate integrally with the input shaft 15 , a carrier 30 supporting a pinion 22 and connected to rotate integrally with the output shaft 16 , and a case 50 .
- a ring gear 25 is fixed to the ring gear 25.
- the sun gear 21 is formed at the end of the input shaft 15.
- the outer peripheral portion of the ring gear 25 is fixed to the case 50.
- ring gear 25 is an internal gear.
- the sun gear 21 and the input shaft 15 that rotate integrally function as the input member 10n of the drive transmission device 10.
- the carrier 30 and the output shaft 16 that rotate integrally function as the output member 10t of the drive transmission device 10.
- the input member 10n of the drive transmission device 10 and the input shaft 15 may be separate members and may be drivingly connected to each other.
- the output member 10t of the drive transmission device 10 and the output shaft 16 may be separate members and may be drivingly connected to each other.
- the direction along the rotational axis Xc of the carrier 30 is defined as the axial direction X.
- the direction perpendicular to the rotational axis Xc is defined as a radial direction R
- the direction of rotation around the rotational axis Xc is defined as a circumferential direction C.
- a direction along the vertical direction is defined as an up-down direction Z.
- the side where the output shaft 16 is arranged with respect to the input shaft 15 (the right side in FIG. 2) is defined as a first axial side X1
- the opposite side is defined as a second axial side X2.
- the planetary gear mechanism 20 may be a single pinion type or a double pinion type.
- a single pinion type planetary gear mechanism is used, and each of the pinions 22 distributed in a plurality along the circumferential direction C is configured to mesh with both the sun gear 21 and the ring gear 25.
- the plurality of pinions 22 are each supported by a pinion shaft 23 fixed to the carrier 30 via a pinion bearing 73.
- each of the plurality of pinions 22 is configured to be freely rotatable around the pinion shaft 23 (that is, freely rotatable) and rotatably around the rotation axis Xc of the carrier 30 (that is, freely revolve).
- a scraping part 35 for scraping up oil inside the case 50 is provided on the outer circumference of the carrier 30.
- the scraping part 35 is formed in the shape of a gear with external teeth formed on the outer peripheral surface of the flange part 32 provided on the carrier 30.
- the scraping part 35 is formed in the shape of a helical gear with external teeth formed on the outer peripheral surface of the flange part 32.
- the helical direction of the helical gear-shaped portion is such that oil is blown toward the first side X1 in the axial direction by the rotation of the scraping portion 35 while the vehicle 11 is moving forward. .
- the flange portion 32 is formed to protrude outward in the radial direction R with respect to the carrier body portion 31.
- the flange portion 32 is formed to protrude outward in the radial direction R with respect to the carrier body portion 31 and to also protrude on the first axial side X1 (right side in FIG. 2).
- the flange portion 32 is formed in an annular shape.
- the flange portion 32 may be integrally formed with the same member as the carrier body portion 31, or may be a separate member from the carrier body portion 31 and connected to rotate integrally with the carrier body portion 31. good.
- the flange portion 32 and the carrier body portion 31 may be fastened together with bolts, or may be integrally fixed by welding or the like.
- the flange portion 32 and the carrier body portion 31 may be connected to rotate integrally by spline engagement or the like.
- the flange portion 32 may be fixed to the carrier body portion 31 such that the central axis of the scraping portion 35 is coaxial with the rotation axis Xc of the carrier body portion 31, or the central axis of the scraping portion 35 may be
- the flange portion 32 may be fixed to the carrier body portion 31 such that the flange portion 32 has an eccentric positional relationship with respect to the rotation axis Xc of the carrier body portion 31.
- FIG. 4 is an enlarged view of the upper part of the drive transmission device 10.
- FIG. 5 is an enlarged view of the lower part of the drive transmission device 10. As shown in FIG.
- the scraping part 35 is arranged on one side of the ring gear 25 in the axial direction X.
- the side on which the scraping portion 35 is arranged is the first axial side X1
- the opposite side is the second axial side X2.
- the scraping portion 35 and the ring gear 25 are arranged adjacent to each other in the axial direction X without any other member being sandwiched between them.
- another member such as a rib provided on the case 50 or another member, may be arranged between the scraping part 35 and the ring gear 25.
- the lower end Tf of the rotational trajectory of the scraping unit 35 is located below the lower end Tp of the revolutional trajectory of the pinion 22 Z2.
- the lower end Tf is shown as the lower end of the outer edge Cf on the rotation locus of the rake-up portion 35
- the lower end Tp is shown as the lower end of the tip circle Cp on the revolution locus of the pinion 22.
- the scraping portion 35 is formed on the outer circumferential surface of the flange portion 32 that protrudes outward in the radial direction R with respect to the carrier body portion 31. Therefore, the scraping portion 35 is provided at the outermost peripheral edge of the carrier 30.
- the scraping portion 35 is located at the outermost peripheral edge of the carrier 30. It does not need to be provided, and may be provided, for example, on the outer periphery of a portion of the carrier 30 that is located inside the outermost periphery.
- the input shaft 15 is integrally formed with the sun gear 21 of the planetary gear mechanism 20.
- the output shaft 16 is connected to the carrier 30 so as to rotate together with the carrier 30.
- the output shaft 16 includes an output shaft main body portion 16a formed in the shape of a shaft, and an output shaft flange portion 16b formed in the shape of a flange.
- the output shaft flange portion 16b is formed to protrude outward in the radial direction R from the end of the output shaft main body portion 16a on the second axial side X2. Further, the output shaft flange portion 16b is formed into a disk shape.
- a first spline engagement portion 16c for connecting to the carrier 30 is formed on the outer peripheral surface of the output shaft flange portion 16b. Further, in this embodiment, a second spline engagement portion 32a that engages with the first spline engagement portion 16c is formed on the inner circumferential surface of the flange portion 32 of the carrier 30.
- the flange portion 32 is formed to protrude toward the first axial side X1 with respect to the carrier body portion 31.
- a second spline engagement portion 32 a is formed on the inner peripheral surface of the protruding portion of the flange portion 32 .
- a snap ring 36 is locked to the second spline engagement portion 32a.
- the snap ring 36 is disposed on the first axial side X1 with respect to the first spline engagement portion 16c, and the output shaft flange portion 16b is sandwiched between the snap ring 36 and the carrier body portion 31 in the axial direction X. It is arranged according to the following.
- the carrier main body portion 31, the flange portion 32, and the output shaft flange portion 16b are integrated.
- the parking gear 40 is arranged on the second axial side X2 with respect to the carrier 30 and the ring gear 25.
- the parking gear 40 is fixed to the input shaft 15 so as to rotate integrally with the input shaft 15.
- the parking gear 40 is connected to the input shaft 15 by spline engagement so as to rotate together with the input shaft 15.
- An oil supply path Rt is formed in the case 50 to flow the oil scraped up by the scraping portion 35 to the location 70 requiring lubrication.
- the oil supply path Rt may be configured by a groove or rib provided on the inner surface of the case 50, a through hole formed in the case 50, the inner surface of the case 50 itself, or a combination of some or all of these.
- the fourth communicating oil passage 64 and the like function as an oil supply route Rt.
- the lubrication required portion 70 includes a first input bearing 71a and a second input bearing 71b, which are a pair of input bearings 71 that rotatably support the input shaft 15 with respect to the case 50, and the output shaft 16.
- the lubrication-requiring locations 70 include a pinion bearing 73 that rotatably supports the pinion 22 with respect to the carrier 30.
- a meshing portion between the pinion 22 and the ring gear 25, a meshing portion between the pinion 22 and the sun gear 21, etc. may be included.
- the input bearing 71 and the output bearing 72 are also included in the locations 70 requiring lubrication.
- the case 50 includes a first case part 50a and a second case part 50b that are liquid-tightly fastened to each other with bolts 42.
- the internal space of the case 50 is a liquid-tight space, and the lower part of the case 50 serves as an oil storage section for storing oil.
- the oil in the case 50 that is, the oil in the oil storage section, is scooped up by the scooping section 35 and is supplied to the lubrication required location 70 through the oil supply path Rt.
- the case 50 is a non-rotating member.
- the oil level height L1 in the case 50 when the vehicle 11 is in a steady running state is lower than the lower end Tp of the revolution locus of the pinion 22 and lower than the lower end Tf of the rotation locus of the scraping part 35.
- the oil amount is set so that the upper side Z1 is also reached.
- the steady running state is a state in which each rotating member inside the drive transmission device 10 is rotating at a speed that stabilizes the oil level height L1 in the case 50 as the vehicle 11 runs. be. With such a setting, the stirring of oil by the pinion 22 can be suppressed to a small level.
- the oil level height L2 in the case 50 when the vehicle 11 is stopped for a long period of time is set to be equal to or higher than the pinion bearing 73.
- the long-term stopped state is a state in which most of the oil in the case 50 falls into the oil storage part and the oil level height L1 in the case 50 is the highest.
- the case 50 includes an opposing inner circumferential surface 53 that faces the scraping portion 35 from the outside in the radial direction R.
- This opposing inner circumferential surface 53 is arranged above the rotational axis Xc at an upper side Z1, and is arranged so as to intersect with a tangent to the outer edge Cf of the rotation locus of the scraping part 35 when viewed in the axial direction along the axial direction X. It has a receiving surface 54a.
- an oil receiving surface 54a By providing such an oil receiving surface 54a, the oil scraped up by the scraping part 35 is received at the upper side Z1 of the scraping part 35, and the oil is flowed from there along the oil supply route Rt using gravity. be able to.
- the oil receiving surface 54a is arranged to be perpendicular to the tangent to the outer edge Cf. More specifically, the oil receiving surface 54a is arranged to be perpendicular to the tangent at the upper end of the outer edge Cf.
- an upper recess 54 is formed in the opposing inner circumferential surface 53 in which a portion facing the upper end region of the rotation locus of the scraping portion 35 is recessed upward Z1 compared to other portions, and the periphery of the upper recess 54 is recessed.
- the side surface in the direction serves as an oil receiving surface 54a.
- oil receiving surfaces 54a are provided on both sides of the upper recess 54 in the circumferential direction C, but only on one side in the circumferential direction C, for example, the oil receiving surface 54a is provided in the direction in which the oil scraped up during forward rotation hits. Only one may be provided.
- the case 50 is disposed on the first axial side X1 with respect to the carrier 30, and includes a side wall surface 55 facing the second axial side X2.
- An oil groove 57 is formed in this side wall surface 55 and communicates with a location 70 requiring lubrication.
- the oil groove 57 is open toward the second axial side X2.
- the oil receiving surface 54a and the oil groove 57 are connected to form an oil supply path Rt communicating with the location 70 requiring lubrication.
- the oil groove 57 is formed in the shape of a concave groove that is recessed toward the first axial side X1 with respect to the side wall surface 55.
- the drive transmission device 10 further includes an oil receiver 80.
- the oil receiver 80 is fixed to the carrier 30. Further, the oil receiving portion 80 is disposed on the inner side in the radial direction R than the scraping portion 35 and is formed to open toward the inner side in the radial direction R. Further, in this embodiment, the scraping part 35 is arranged between the ring gear 25 and the side wall surface 55 in the axial direction X, and the oil receiving part 80 is arranged between the carrier 30 and the side wall surface 55 in the axial direction X. It is located.
- the oil receiving portion 80 may be directly fixed to the carrier 30, or may be indirectly fixed to the carrier 30 with an integrally rotating member interposed therebetween.
- the oil receiver 80 is fixed to the output shaft flange 16b that rotates integrally with the carrier 30. Furthermore, in this embodiment, the oil receiving portion 80 is formed continuously over the entire circumference. More specifically, the oil receiving portion 80 is formed in an annular shape, and as shown in FIGS. 4 and 5, the cross-sectional shape becomes axially first as it goes inward in the radial direction It has a shape that is inclined toward the side X1.
- the case 50 is formed so as to protrude from the side wall surface 55 toward the second axial side X2 on the inner side of the oil receiving portion 80 in the radial direction R, and the case 50 is formed so as to protrude from the side wall surface 55 toward the second axial side X2. It further includes a protrusion 58 arranged to overlap the receiving part 80. In this embodiment, the protruding portion 58 is formed to protrude from the side wall surface 55 toward the second axial side X2.
- the protruding portion 58 includes a protruding outer circumferential surface 58a facing outward in the radial direction R, and a protruding end surface 58b, which is an end surface of the protruding portion 58 facing the second axial side X2.
- a portion of the second cylindrical portion 52 of the case 50 that is closer to the second axial side X2 than the side wall surface 55 is the protruding portion 58 .
- an oil cutting groove 59 that opens toward the lower side Z2 is provided in a portion of the protruding outer circumferential surface 58a facing the lower side Z2 and adjacent to the first axial side X1 with respect to the protruding end surface 58b.
- the carrier 30 is formed with an in-carrier oil passage 38 that communicates the oil receiver 80 and the pinion bearing 73. Therefore, the oil scraped up by the scraping part 35 flows toward the lower side Z2 along the side wall surface 55 or the oil groove 57 and reaches the protruding outer circumferential surface 58a.
- the oil that has reached the protruding outer circumferential surface 58a flows toward the lower side Z2 in the circumferential direction C along the protruding outer circumferential surface 58a, and also flows toward the lower side Z2 along the protruding end surface 58b.
- the oil falling from the protruding outer circumferential surface 58a or the protruding end surface 58b is received by the oil receiving portion 80.
- the oil cutting grooves 59 provided on the protruding outer circumferential surface 58a prevent the oil that has reached the lower ends of the protruding outer circumferential surface 58a and the protruding end surface 58b from flowing toward the side wall surface 55 on the lower side Z2 than the protruding portion 58. fulfill the function of The oil received by the oil receiver 80 is guided to the carrier oil passage 38 by the shape of the oil receiver 80 and is supplied to the pinion bearing 73 through the carrier oil passage 38 .
- the carrier oil passage 38 includes a space 23a formed in the pinion shaft 23, an axial through hole 38a that communicates the space 23a with the oil receiver 80, and a space 23a and the pinion shaft.
- a radial through hole 38b that communicates with the outer circumferential surface of 23 in the radial direction R is provided.
- the oil discharged from the radial through hole 38b is supplied to the pinion bearing 73.
- the axial through hole 38a passes through the carrier body portion 31 and the output shaft flange portion 16b in the axial direction X.
- the case 50 includes a first cylindrical portion 51 that supports the input bearing 71 from the outside in the radial direction R, and a second cylindrical portion that supports the output bearing 72 from the outside in the radial direction R.
- a shaped portion 52 is provided.
- a first communication oil passage 61 is formed in the first cylindrical portion 51 .
- the first communicating oil passage 61 communicates between a portion of the outer circumferential surface of the first cylindrical portion 51 facing upward Z1 and an inner circumferential surface that supports the input bearing 71 .
- a second communication oil passage 62 is formed in the second cylindrical portion 52, which communicates between the portion of the outer circumferential surface of the second cylindrical portion 52 facing the upper side Z1 and the inner circumferential surface that supports the output bearing 72.
- the oil that has entered the second communicating oil passage 62 then reaches the output bearing 72.
- the output bearing 72 can be lubricated.
- each bearing can be lubricated, for example, without providing oil passages inside the input shaft 15 and the output shaft 16.
- the oil supply path Rt for the oil that reaches the first cylindrical portion 51 may be a path that runs along the inner surface of the case 50, or a path that passes through a through hole or an oil groove (not shown) in the case 50. Also good.
- the oil scooped up by the parking gear 40 may reach the input bearing 71 via the first communication oil passage 61.
- the first cylindrical portion 51 includes a third communication oil passage 63 that communicates between the portion of the outer circumferential surface of the first cylindrical portion 51 facing the lower side Z2 and the inner circumferential surface that supports the input bearing 71. is formed. Further, a fourth communication oil passage 64 is formed in the second cylindrical portion 52, which communicates the portion of the outer circumferential surface of the second cylindrical portion 52 facing the lower side Z2 with the inner circumferential surface that supports the output bearing 72. has been done.
- the first communication oil passage 61 and the third communication oil passage 63 are provided on the inner peripheral surface of the first cylindrical portion 51 so as to open on opposite sides in the axial direction X with the second input bearing 71b interposed therebetween. ing. Further, the second communication oil passage 62 and the fourth communication oil passage 64 are configured to open on opposite sides in the axial direction It is provided.
- the oil supplied from the first communication oil passage 61 to lubricate the second input bearing 71b is sent to the lower side Z2 than the first cylindrical part 51 via the third communication oil passage 63. Can be discharged.
- the oil supplied from the second communication oil passage 62 and after lubricating the first output bearing 72a is discharged to the lower side Z2 than the second cylindrical part 52 via the fourth communication oil passage 64. I can do it. Therefore, the oil after lubricating the second input bearing 71b and the first output bearing 72a can be appropriately discharged and circulated within the case 50.
- the oil supplied from the first communicating oil passage 61 to lubricate the first input bearing 71a is discharged from the end of the first axially first side X1 of the first cylindrical portion 51.
- the oil supplied from the second communicating oil passage 62 and lubricating the second output bearing 72b is discharged from the end of the second cylindrical portion 52 on the second axial side X2.
- an input side oil seal 81 is arranged between the inner circumferential surface of the first cylindrical portion 51 and the outer circumferential surface of the input shaft 15 to prevent oil from leaking out of the case 50.
- an output side oil seal 82 is arranged between the inner circumferential surface of the second cylindrical portion 52 and the outer circumferential surface of the output shaft 16 to prevent oil from leaking out of the case 50.
- the scraping part 35 is arranged on one side of the ring gear 25 in the axial direction
- An oil supply path Rt is formed in the case 50 and flows the oil scraped up by the scraping portion 35 to the location 70 requiring lubrication.
- the opposing inner circumferential surface 53 is disposed above the rotation axis Xc at an upper side Z1, and is arranged so as to intersect with a tangent to the outer edge Cf of the rotation locus of the scraping part 35 when viewed in the axial direction along the axial direction X.
- An oil receiving surface 54a is provided.
- the parts 70 requiring lubrication include a pinion bearing 73 that rotatably supports the pinion 22 with respect to the carrier 30, and the carrier 30 includes a carrier that communicates the oil receiver 80 with the pinion bearing 73.
- An inner oil passage 38 is formed.
- the oil groove 57 opens toward the second axial side It is formed in a gear shape and is oriented such that oil is blown toward the first side X1 in the axial direction by rotation of the scraping portion 35 while the vehicle 11 is moving forward.
- a drive transmission device 10 according to a second embodiment will be described below with reference to FIG. 6.
- the drive transmission device 10 includes an oil pump 110, the third communicating oil passage 63 is not formed in the first cylindrical part 51, and the fourth communicating oil passage 63 is not formed in the second cylindrical part 52.
- This embodiment differs from the first embodiment in that a communicating oil passage 64 is not formed. Below, the explanation will focus on the differences from the first embodiment. Note that points not particularly described are the same as those in the first embodiment.
- the drive transmission device 10 includes an oil pump 110 that sucks oil in the case 50 and supplies oil to the oil supply path Rt.
- the oil pump 110 is supported by a first case part 50a and a second case part 50b. It is preferable that the oil pump 110 supplies oil to the oil supply path Rt via an oil cooler (not shown). Further, a suction port (not shown) through which the oil pump 110 sucks oil in the case 50 is arranged at a lower side Z2 than the oil level height L1 in the case 50 when the vehicle 11 is in a steady running state. is preferred.
- the parking pole 41 that rotates around the rotation axis Xc selectively engages with the parking gear 40. Furthermore, in this embodiment, the oil pump 110 is arranged so as to overlap the parking gear 40, the parking pole 41, or the parking gear 40 and the parking pole 41 when viewed in the radial direction R.
- the oil pump 110 is a mechanical oil pump that is driven as the input shaft 15 or the output shaft 16 rotates.
- the drive transmission device 10 includes a pump drive gear 111 that rotates integrally with the carrier 30 and drives the oil pump 110.
- the pump drive gear 111 is fixed to the carrier body 31 by welding or the like. Further, the pump drive gear 111 is disposed between the carrier body 31 and the parking gear 40 in the axial direction X.
- the oil pump 110 is configured to supply oil to the oil supply path Rt while the vehicle 11 is moving forward.
- the scraping portion 35 is formed in the shape of an external helical gear formed on the outer peripheral surface of the flange portion 32 provided on the carrier 30, and is rotated by the rotation of the scraping portion 35 while the vehicle 11 is moving backward. It is formed in such a direction that the oil is blown toward the first side X1 in the axial direction. In this way, while the vehicle 11 is moving forward, the oil pump 110 can supply a large amount of oil to the oil supply path Rt, and even while the vehicle 11 is moving backward, the oil scraped up by the scooping part 35 can be removed from the oil groove 57. A large amount of oil can be supplied to the oil supply path Rt.
- the input shaft 15 is supported by a pair of input bearings 71 arranged on both sides of the sun gear 21 in the axial direction X.
- the output shaft 16 is supported by a double-row output bearing 72.
- the outer ring of the output bearing 72 is fixed to the case 50 by a locking member 78.
- the locking member 78 is disposed on the second axial side X2 of the output bearing 72 and holds the outer ring of the output bearing 72 between the wall surface of the case 50 on the first axial side X1 of the output bearing 72.
- the output shaft 16 and the carrier 30 are fixed by welding or the like so that they rotate together.
- the output shaft flange portion 16b and the flange portion 32 are fixed by welding or the like, and the flange portion 32 and the carrier body portion 31 are fixed by welding or the like.
- the output shaft flange portion 16b supports the pinion shaft 23 and functions as a part of the carrier 30. In other words, a portion of the output shaft 16 functions as a portion of the carrier 30.
- the protruding portion 58 is formed to protrude from the side wall surface 55 toward the second axial side X2 on the inner side of the oil receiving portion 80 in the radial direction R. Further, a female thread is formed on the inner diameter side of the protrusion 58, and is screwed into a male thread formed on the outer peripheral surface of the cylindrical locking member 78. Further, an oil passage (a spline in the illustrated example) is formed on the inner circumferential side of the cylindrical locking member 78 to allow oil supplied to the output bearing 72 to flow into the oil receiver 80 . The oil received by the oil receiver 80 is supplied to the space 23a formed within the pinion shaft 23 due to the shape of the oil receiver 80.
- the pinion 22 is formed with a pinion through hole 38c that communicates the inner circumferential surface of the pinion 22 with the outer circumferential surface of the pinion 22 in the radial direction R.
- the oil supplied to the pinion bearing 73 is supplied to the meshing portion between the sun gear 21 and the pinion 22 through the pinion through hole 38c.
- the drive transmission device 10 is mounted on a vehicle 11 equipped with a drive source 12 such as a rotating electrical machine.
- the drive source 12 is not limited to a rotating electrical machine, but may be an internal combustion engine or a hybrid of an internal combustion engine and a rotating electrical machine. That is, the vehicle 11 may be a car that uses only an internal combustion engine as the drive source 12, a hybrid car that uses the internal combustion engine and a rotating electric machine as the drive source 12, an electric car, or the like.
- this drive transmission device 10 may be mounted on a vehicle 11 other than an automobile.
- the drive transmission device 10 is also suitable for use in an in-wheel motor type drive device, as shown in FIG. 7, for example.
- the configuration in which the scraping portion 35 is formed in the shape of a gear with external teeth has been described as an example.
- the scraping part 35 may be formed such that unevenness in the axial direction It may be provided with both unevenness in the direction R and unevenness in the axial direction X, and the unevenness may be formed so as to be lined up in the circumferential direction C.
- the oil receiving portion 80 is continuously formed over the entire circumference.
- a configuration may be adopted in which the oil receiving portion 80 is provided only in the vicinity of the axial through hole 38a.
- the oil receiver 80 is a separate member from the carrier 30 and is fixed to the carrier 30.
- the present invention is not limited to this.
- the oil receiving portion 80 may be formed integrally with the carrier 30.
- the drive transmission device 10 does not need to include the oil receiver 80.
- the lubrication-requiring parts 70 are described as including the input bearing 71, the output bearing 72, and the pinion bearing 73, but these are not included in the lubrication-requiring parts 70. You don't have to.
- the case 50 includes the opposing inner peripheral surface 53, the upper recess 54, the oil receiving surface 54a, the side wall surface 55, the oil groove 57, and the protrusion 58 as the oil supply path Rt.
- a configuration in which the protruding outer circumferential surface 58a, the protruding end surface 58b, and the first to fourth communicating oil passages 61 to 64 are provided has been described as an example.
- the oil supply route Rt may be configured by only a part of these without being limited to such a configuration.
- the oil supply path Rt may be configured only by the inner surface of the case 50 without providing a groove or a through hole.
- the explanation has been given by taking as an example a configuration in which the scraping portion 35 is formed in such a direction as to fly toward the first side X1.
- the rotation of the rake-up portion 35 while the vehicle 11 is moving backward in the first embodiment causes the rake-up portion 35 to rotate while the vehicle 11 is moving forward in the second embodiment.
- the scraping portion 35 may be formed in such a direction that the oil is blown toward the first side X1 in the axial direction by the rotation of the portion 35 .
- the drive transmission device 10 includes the oil pump 110, and the oil pump 110 is driven by the pump drive gear 111 while the vehicle 11 is moving forward.
- the present invention is not limited to such a configuration, and, for example, the drive transmission device 10 in the second embodiment may not include the oil pump 110.
- the drive transmission device 10 may include the oil pump 110 in the first embodiment.
- the oil pump 110 may be driven with the rotation of the input shaft 15 or the output shaft 16 via a chain, a belt, or the like instead of parallel gears.
- the oil pump 110 may be an electric oil pump.
- oil may be supplied to the oil supply path Rt by the oil pump 110 while the vehicle 11 is moving backward, or while the vehicle 11 is moving forward or backward. Further, for example, oil may be supplied to the oil supply path Rt by both the oil pump 110 and the scraping section 35 while the vehicle 11 is moving forward or backward.
- the input shaft (15) is drivingly connected to the drive source (12), the output shaft (16) is drivingly connected to the wheels (14), and the rotation of the input shaft (15) is decelerated and the output shaft is
- a drive transmission device (10) comprising a planetary gear mechanism (20) for deceleration that transmits data to the planetary gear mechanism (20), and a case (50) that accommodates the planetary gear mechanism (20).
- a sun gear (21) connected to rotate integrally with the input shaft (15), and a carrier supporting the pinion (22) and connected to rotate integrally with the output shaft (16).
- the scraping part (35) is provided with a ring gear (25), with the direction along the rotation axis (Xc) of the carrier (30) being the axial direction (X), and the direction along the vertical direction being the vertical direction (Z).
- the lower end (Tf) of the rotation trajectory of the scraping part (35) is located below (Z2) than the lower end (Tp) of the revolution trajectory of the pinion (22).
- An oil supply path (Rt) is formed in the case (50) to flow the oil scraped up by the scraping portion (35) to the location requiring lubrication (70).
- the scraping section can scrape up the oil and supply oil to areas that require lubrication, so the pinion is not submerged in oil.
- the ratio it is easy to suppress oil agitation by the pinion. Therefore, the oil can be appropriately scraped up by the scraping section while minimizing the rotational resistance of the planetary gear mechanism due to stirring of the oil.
- the scraping part (35) is formed in the shape of a gear with external teeth formed on the outer peripheral surface of the flange part (32) provided on the carrier (30), and is perpendicular to the rotation axis (Xc).
- the direction is defined as the radial direction (R), and the direction of rotation around the rotational axis (Xc) is defined as the circumferential direction (C).
- the opposing inner circumferential surfaces (53) are disposed above (Z1) than the rotation axis Xc, and the raking portion ( 35) is preferably provided with an oil receiving surface (54a) arranged to intersect with a tangent to the outer edge (Cf) in the rotation locus.
- the oil scraped up by the scraping part can be received above the rotational axis of the carrier, and from there, the oil can be flowed along the oil supply path to the locations requiring lubrication using gravity. Therefore, oil can be appropriately supplied to locations that require lubrication without using an oil pump or the like.
- the side where the scraping part (35) is arranged with respect to the ring gear (25) is defined as the first axial side (X1), and the opposite side thereof is defined as the second axial side. (X2), and the direction perpendicular to the rotational axis (Xc) is defined as the radial direction (R).
- the case (50) is arranged on the first axial side (X1) with respect to the carrier (30) and on the second axial side (X1) with respect to the carrier (30).
- the scraping part (35) is arranged between the ring gear (25) and the side wall surface (55) in the axial direction X, and the oil receiving part (80) (30) and the side wall surface (55) in the axial direction X, and is fixed to the carrier (30).
- a protrusion formed to protrude from the side wall surface (55) toward the second axial side (X2) and arranged to overlap with the oil receiver (80) when viewed in the radial direction (R).
- the lubrication required portion (70) includes a pinion bearing (73) that rotatably supports the pinion (22) relative to the carrier (30), and the carrier (30) includes a portion (58) that requires lubrication.
- an in-carrier oil passage (38) is formed that communicates the oil receiver (80) and the pinion bearing (73).
- the oil scraped up by the scraping part flows from the side wall surface to the protruding part, and the oil that flows along the outer surface of the protruding part and then falls is received by the oil receiving part. Oil is then supplied to the pinion bearing from the oil receiver. Therefore, the oil scraped up by the scraping part can appropriately lubricate the pinion bearing that supports the pinion.
- the side where the scraping part (35) is arranged with respect to the ring gear (25) is defined as the first axial side (X1), and the opposite side thereof is defined as the second axial side.
- the case (50) is disposed on the first axial side (X1) with respect to the carrier (30), and includes a side wall surface (55) facing the second axial side (X2).
- the raking portion (35) is formed in the shape of a helical gear with external teeth formed on the outer peripheral surface of the flange portion (32) provided on the carrier (30), and is configured to rotate the scraping portion (35) while the vehicle (11) is moving forward. Accordingly, it is preferable that the oil is oriented such that the oil is blown toward the first side (X1) in the axial direction.
- the input shaft (71) and the output shaft (72) are arranged coaxially, and the input shaft (71) and the output shaft (72) are arranged side by side in the axial direction (X),
- the parts (70) that require lubrication include an input bearing (71) that rotatably supports the input shaft (71) with respect to the case (50), and an input bearing (71) that rotatably supports the output shaft (72) with respect to the case (50).
- the case (50) includes an output bearing (72) to support, and the direction perpendicular to the rotation axis (Xc) is defined as the radial direction (R), and the case (50) supports the input bearing (71) on the outside in the radial direction (R).
- a cylindrical first cylindrical part (51) that supports the output bearing (72) from the outside in the radial direction R is provided.
- the first cylindrical portion (51) has a first communicating oil that communicates between the portion of the outer peripheral surface of the first cylindrical portion (51) facing upward (Z1) and the inner peripheral surface that supports the input bearing (71).
- a channel (61) is formed.
- the second cylindrical portion (52) also has a second cylindrical portion that communicates between the portion of the outer circumferential surface of the second cylindrical portion (52) facing upward (Z1) and the inner circumferential surface that supports the output bearing (72).
- a communicating oil passage (62) is formed.
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Abstract
A drive transmission device (10) comprises: a speed-reduction planetary gear mechanism (20) for reducing the speed of rotation of an input shaft (15) and transmitting the speed-reduced rotation to an output shaft (16); and a case (50) that stores the planetary gear mechanism (20). A scraping-up part (35) for scraping-up oil in the case (50) is provided to the outer peripheral part of a carrier (30) of the planetary gear mechanism (20). The scraping-up part (35) is disposed on one side in an axial direction (X) with respect to a ring gear (25). The lower end (Tf) of the scraping-up part (35) in a rotation trajectory is disposed on a lower side (Z2) lower than the lower end (Tp) of a pinion (22) in the rotation trajectory. An oil supply path (Rt) through which the oil scraped-up by the scraping-up part (35) flows to a lubrication necessary part (70) is formed in the case (50).
Description
本発明は、遊星歯車機構を備えた車両用駆動伝達装置に関する。
The present invention relates to a vehicle drive transmission device equipped with a planetary gear mechanism.
遊星歯車機構とケース内の油を掻き上げるための掻き上げ部とを備える車両用駆動伝達装置が知られている。特許文献1には、撹拌室内の油を掻き上げるためにキャリヤと共に回転する撹拌翼を備えた車両用駆動伝達装置が記載されている。
A vehicle drive transmission device is known that includes a planetary gear mechanism and a scraping part for scraping up oil in a case. Patent Document 1 describes a vehicle drive transmission device including a stirring blade that rotates together with a carrier to scrape up oil in a stirring chamber.
しかし、特許文献1に記載の車両用駆動伝達装置は、撹拌室内の油を撹拌翼で掻き上げる構成であって、ピニオンの公転軌跡の下端が撹拌翼の下端よりも下側に配置されているため、ピニオンが油に浸かる割合が大きくなり易く、油の撹拌量が多くなり易いという課題があった。
However, the vehicle drive transmission device described in Patent Document 1 has a configuration in which the oil in the stirring chamber is scraped up by the stirring blade, and the lower end of the revolution trajectory of the pinion is arranged below the lower end of the stirring blade. Therefore, there was a problem in that the proportion of the pinion immersed in oil tends to increase, and the amount of oil agitation tends to increase.
そこで、遊星歯車機構の回転を利用して油を掻き上げる構成において、ピニオンによる油の撹拌を少なく抑えることができる技術の実現が望まれる。
Therefore, in a configuration in which oil is scraped up using the rotation of a planetary gear mechanism, it is desired to realize a technology that can suppress the agitation of oil by the pinion.
上記に鑑みた車両用駆動伝達装置の特徴構成は、駆動源に駆動連結される入力軸と、車輪に駆動連結される出力軸と、前記入力軸の回転を減速して前記出力軸に伝達する減速用の遊星歯車機構と、前記遊星歯車機構を収容するケースと、を備えた車両用駆動伝達装置であって、前記遊星歯車機構は、前記入力軸と一体的に回転するように連結されたサンギヤと、ピニオンを支持すると共に前記出力軸と一体的に回転するように連結されたキャリヤと、前記ケースに固定されたリングギヤと、を備え、前記キャリヤの外周部に、前記ケース内の油を掻き上げるための掻き上げ部が設けられ、前記キャリヤの回転軸心に沿う方向を軸方向とし、鉛直方向に沿う方向を上下方向として、前記掻き上げ部は、前記リングギヤに対して軸方向の一方側に配置され、前記掻き上げ部の回転軌跡の下端が、前記ピニオンの公転軌跡の下端よりも下側に配置され、前記ケースに、前記掻き上げ部により掻き上げられた油を潤滑必要箇所へ流す油供給経路が形成されている。
In view of the above, the characteristic configuration of a vehicle drive transmission device includes an input shaft that is drivingly connected to a drive source, an output shaft that is drivingly connected to a wheel, and a system that decelerates the rotation of the input shaft and transmits it to the output shaft. A vehicle drive transmission device comprising a planetary gear mechanism for deceleration and a case accommodating the planetary gear mechanism, the planetary gear mechanism being connected to the input shaft so as to rotate integrally with the input shaft. a sun gear; a carrier that supports a pinion and is connected to rotate integrally with the output shaft; and a ring gear that is fixed to the case; A scraping part for scraping up is provided, the direction along the rotational axis of the carrier is the axial direction, and the direction along the vertical direction is the vertical direction, and the scraping part is arranged in one direction in the axial direction with respect to the ring gear. The lower end of the rotational trajectory of the scraping part is arranged below the lower end of the revolving trajectory of the pinion, and the oil scraped up by the scraping part is directed to areas requiring lubrication in the case. An oil supply path is formed to allow the oil to flow.
この特徴構成によれば、油面がピニオンの公転軌跡の下端よりも下側にある場合でも掻き上げ部により油を掻き上げて潤滑必要箇所に油を供給することができるので、ピニオンが油に浸かる割合を少なくしてピニオンによる油の撹拌を少なく抑え易い。従って、油の撹拌による遊星歯車機構の回転抵抗を少なく抑えつつ、掻き上げ部による油の掻き上げを適切に行うことができる。
According to this characteristic configuration, even if the oil level is below the lower end of the pinion's orbit, the scraping part can scrape up the oil and supply oil to the parts that require lubrication, so the pinion can It is easy to reduce the oil agitation caused by the pinion by reducing the immersion ratio. Therefore, the oil can be appropriately scraped up by the scraping section while minimizing the rotational resistance of the planetary gear mechanism due to stirring of the oil.
本開示に係る技術のさらなる特徴と利点は、図面を参照して記述する以下の例示的かつ非限定的な実施形態の説明によってより明確になる。
Further features and advantages of the technology according to the present disclosure will become clearer from the following description of exemplary and non-limiting embodiments, written with reference to the drawings.
〔第1の実施形態〕
以下では、第1の実施形態に係る車両用駆動伝達装置(以下、駆動伝達装置)10について、図1から図5を参照して説明する。 [First embodiment]
Below, a vehicle drive transmission device (hereinafter referred to as a drive transmission device) 10 according to a first embodiment will be described with reference to FIGS. 1 to 5.
以下では、第1の実施形態に係る車両用駆動伝達装置(以下、駆動伝達装置)10について、図1から図5を参照して説明する。 [First embodiment]
Below, a vehicle drive transmission device (hereinafter referred to as a drive transmission device) 10 according to a first embodiment will be described with reference to FIGS. 1 to 5.
図1は、駆動伝達装置10が搭載された車両11の模式図である。図2は、駆動伝達装置10の断面図である。図3は、駆動伝達装置10を軸方向第1側X1側から視た側面の模式図である。駆動伝達装置10は、例えば、回転電機等の駆動源12と、差動歯車装置13と、車輪14とを備えた車両11に搭載される。差動歯車装置13は、駆動源12の側から駆動伝達装置10を介して入力された駆動力を一対の車輪14に分配する。なお、本願において「回転電機」は、モータ(電動機)、ジェネレータ(発電機)、及び必要に応じてモータ及びジェネレータの双方の機能を果たすモータ・ジェネレータのいずれをも含む概念として用いている。
FIG. 1 is a schematic diagram of a vehicle 11 equipped with a drive transmission device 10. FIG. 2 is a sectional view of the drive transmission device 10. FIG. 3 is a schematic side view of the drive transmission device 10 viewed from the first axial side X1. The drive transmission device 10 is mounted on a vehicle 11 that includes a drive source 12 such as a rotating electric machine, a differential gear device 13, and wheels 14, for example. The differential gear device 13 distributes the driving force input from the drive source 12 via the drive transmission device 10 to the pair of wheels 14 . Note that in this application, the term "rotating electric machine" is used as a concept that includes a motor (electric motor), a generator (generator), and, if necessary, a motor/generator that functions as both a motor and a generator.
駆動伝達装置10は、駆動源12に駆動連結される入力軸15と、車輪14に駆動連結される出力軸16と、入力軸15の回転を減速して出力軸16に伝達する減速用の遊星歯車機構20と、遊星歯車機構20を収容するケース50と、を備えている。本実施形態では、入力軸15と出力軸16とが同軸上に配置されていると共に、入力軸15と出力軸16とが後述の軸方向Xに並んで配置されている。また、本実施形態では、入力軸15が入力軸受71によりケース50に対して回転自在に支持されている。また、出力軸16が出力軸受72によりケース50に対して回転自在に支持されている。図示の例では、入力軸15は、一対の入力軸受71により支持されている。また、出力軸16は、一対の出力軸受72により支持されている。
The drive transmission device 10 includes an input shaft 15 drivingly connected to a drive source 12, an output shaft 16 drivingly connected to the wheels 14, and a deceleration planet that decelerates the rotation of the input shaft 15 and transmits it to the output shaft 16. It includes a gear mechanism 20 and a case 50 that accommodates the planetary gear mechanism 20. In this embodiment, the input shaft 15 and the output shaft 16 are arranged coaxially, and the input shaft 15 and the output shaft 16 are arranged side by side in the axial direction X, which will be described later. Further, in this embodiment, the input shaft 15 is rotatably supported with respect to the case 50 by an input bearing 71. Further, the output shaft 16 is rotatably supported with respect to the case 50 by an output bearing 72. In the illustrated example, the input shaft 15 is supported by a pair of input bearings 71. Further, the output shaft 16 is supported by a pair of output bearings 72.
なお、本願において、「駆動連結」とは、2つの回転要素が駆動力を伝達可能に連結された状態を指し、当該2つの回転要素が一体的に回転するように連結された状態、或いは当該2つの回転要素が一又は二以上の伝動部材を介して駆動力を伝達可能に連結された状態を含む概念として用いている。このような伝動部材としては、回転を同速で又は変速して伝達する各種の部材が含まれ、例えば、軸、歯車機構、ベルト、チェーン等が含まれる。また、このような伝動部材として、回転及び駆動力を選択的に伝達する係合装置、例えば摩擦係合装置や噛み合い式係合装置等が含まれていてもよい。
In addition, in this application, "drive connection" refers to a state in which two rotating elements are connected so that driving force can be transmitted, and a state in which the two rotating elements are connected so that they rotate integrally, or a state in which the two rotating elements are connected so that they rotate integrally. It is used as a concept that includes a state in which two rotating elements are connected so that driving force can be transmitted via one or more transmission members. Such transmission members include various members that transmit rotation at the same speed or at variable speeds, and include, for example, shafts, gear mechanisms, belts, chains, and the like. Furthermore, such a transmission member may include an engagement device that selectively transmits rotation and driving force, such as a friction engagement device or a meshing engagement device.
遊星歯車機構20は、入力軸15と一体的に回転するように連結されたサンギヤ21と、ピニオン22を支持すると共に出力軸16と一体的に回転するように連結されたキャリヤ30と、ケース50に固定されたリングギヤ25と、を備えている。本実施形態では、サンギヤ21は入力軸15の端部に形成されている。本実施形態では、リングギヤ25の外周部がケース50に固定されている。図示の例では、リングギヤ25は内歯車である。また、本実施形態では、一体的に回転するサンギヤ21及び入力軸15が駆動伝達装置10の入力部材10nとして機能している。また、本実施形態では、一体的に回転するキャリヤ30及び出力軸16が駆動伝達装置10の出力部材10tとして機能している。なお、駆動伝達装置10の入力部材10nと入力軸15とが別部材であって、互いに駆動連結されていてもよい。また、駆動伝達装置10の出力部材10tと出力軸16とが別部材であって、互いに駆動連結されていてもよい。
The planetary gear mechanism 20 includes a sun gear 21 connected to rotate integrally with the input shaft 15 , a carrier 30 supporting a pinion 22 and connected to rotate integrally with the output shaft 16 , and a case 50 . A ring gear 25 is fixed to the ring gear 25. In this embodiment, the sun gear 21 is formed at the end of the input shaft 15. In this embodiment, the outer peripheral portion of the ring gear 25 is fixed to the case 50. In the illustrated example, ring gear 25 is an internal gear. Further, in this embodiment, the sun gear 21 and the input shaft 15 that rotate integrally function as the input member 10n of the drive transmission device 10. Further, in this embodiment, the carrier 30 and the output shaft 16 that rotate integrally function as the output member 10t of the drive transmission device 10. Note that the input member 10n of the drive transmission device 10 and the input shaft 15 may be separate members and may be drivingly connected to each other. Further, the output member 10t of the drive transmission device 10 and the output shaft 16 may be separate members and may be drivingly connected to each other.
ここで、キャリヤ30の回転軸心Xcに沿う方向を軸方向Xとする。また、回転軸心Xcに直交する方向を径方向Rとし、回転軸心Xcの周りを周回する方向を周方向Cとする。また、鉛直方向に沿う方向を上下方向Zとする。また、軸方向Xにおける、入力軸15に対して出力軸16が配置されている側(図2の右側)を軸方向第1側X1とし、その反対側を軸方向第2側X2とする。
Here, the direction along the rotational axis Xc of the carrier 30 is defined as the axial direction X. Further, the direction perpendicular to the rotational axis Xc is defined as a radial direction R, and the direction of rotation around the rotational axis Xc is defined as a circumferential direction C. Further, a direction along the vertical direction is defined as an up-down direction Z. Further, in the axial direction X, the side where the output shaft 16 is arranged with respect to the input shaft 15 (the right side in FIG. 2) is defined as a first axial side X1, and the opposite side is defined as a second axial side X2.
遊星歯車機構20は、シングルピニオン式でも、ダブルピニオン式でも良い。本実施形態では、シングルピニオン式の遊星歯車機構となっており、周方向Cに沿って複数分散配置されたピニオン22のそれぞれは、サンギヤ21とリングギヤ25との双方に噛み合うように構成されている。複数のピニオン22は、それぞれキャリヤ30に固定されたピニオンシャフト23によりピニオン軸受73を介して支持されている。これにより、複数のピニオン22はそれぞれピニオンシャフト23周りに回転自在(すなわち自転自在)、且つ、キャリヤ30の回転軸心Xc周りに回転自在(すなわち公転自在)に構成されている。
The planetary gear mechanism 20 may be a single pinion type or a double pinion type. In this embodiment, a single pinion type planetary gear mechanism is used, and each of the pinions 22 distributed in a plurality along the circumferential direction C is configured to mesh with both the sun gear 21 and the ring gear 25. . The plurality of pinions 22 are each supported by a pinion shaft 23 fixed to the carrier 30 via a pinion bearing 73. Thereby, each of the plurality of pinions 22 is configured to be freely rotatable around the pinion shaft 23 (that is, freely rotatable) and rotatably around the rotation axis Xc of the carrier 30 (that is, freely revolve).
キャリヤ30の外周部には、ケース50内の油を掻き上げるための掻き上げ部35が設けられている。本実施形態では、掻き上げ部35は、キャリヤ30に設けられたフランジ部32の外周面に形成された外歯のギヤ状に形成されている。具体的には、掻き上げ部35は、フランジ部32の外周面に形成された外歯のはすばギヤ状に形成されている。ここでは、はすばギヤ状部分のはすばの向きは、車両11の前進中の掻き上げ部35の回転によって、油を軸方向第1側X1に向けて飛ばすような向きとされている。
A scraping part 35 for scraping up oil inside the case 50 is provided on the outer circumference of the carrier 30. In this embodiment, the scraping part 35 is formed in the shape of a gear with external teeth formed on the outer peripheral surface of the flange part 32 provided on the carrier 30. Specifically, the scraping part 35 is formed in the shape of a helical gear with external teeth formed on the outer peripheral surface of the flange part 32. Here, the helical direction of the helical gear-shaped portion is such that oil is blown toward the first side X1 in the axial direction by the rotation of the scraping portion 35 while the vehicle 11 is moving forward. .
キャリヤ30におけるピニオンシャフト23を支持している部分をキャリヤ本体部31とした場合、フランジ部32は、キャリヤ本体部31に対して径方向Rの外側に突出するように形成されている。本実施形態では、フランジ部32は、キャリヤ本体部31に対して径方向Rの外側に突出すると共に、軸方向第1側X1(図2の右側)にも突出するように形成されている。また、フランジ部32は、円環状に形成されている。フランジ部32は、キャリヤ本体部31と同一部材で一体的に形成されていても良く、キャリヤ本体部31と別部材であってキャリヤ本体部31と一体的に回転するように連結されていても良い。例えば、フランジ部32とキャリヤ本体部31とがボルトで締結されていても良く、溶接等により一体的に固定されていても良い。或いは、フランジ部32とキャリヤ本体部31とがスプライン係合等により一体的に回転するように連結されていても良い。また、掻き上げ部35の中心軸がキャリヤ本体部31の回転軸心Xcと同軸となるように、フランジ部32がキャリヤ本体部31に固定されていても良いし、掻き上げ部35の中心軸がキャリヤ本体部31の回転軸心Xcに対して偏心した位置関係となるように、フランジ部32がキャリヤ本体部31に固定されていても良い。本実施形態では、フランジ部32は、キャリヤ本体部31とは別部材であって、溶接によりキャリヤ本体部31と一体化されている。図4は、駆動伝達装置10の上部を拡大して示す図である。図5は、駆動伝達装置10の下部を拡大して示す図である。
When the portion of the carrier 30 that supports the pinion shaft 23 is the carrier body portion 31, the flange portion 32 is formed to protrude outward in the radial direction R with respect to the carrier body portion 31. In this embodiment, the flange portion 32 is formed to protrude outward in the radial direction R with respect to the carrier body portion 31 and to also protrude on the first axial side X1 (right side in FIG. 2). Further, the flange portion 32 is formed in an annular shape. The flange portion 32 may be integrally formed with the same member as the carrier body portion 31, or may be a separate member from the carrier body portion 31 and connected to rotate integrally with the carrier body portion 31. good. For example, the flange portion 32 and the carrier body portion 31 may be fastened together with bolts, or may be integrally fixed by welding or the like. Alternatively, the flange portion 32 and the carrier body portion 31 may be connected to rotate integrally by spline engagement or the like. Further, the flange portion 32 may be fixed to the carrier body portion 31 such that the central axis of the scraping portion 35 is coaxial with the rotation axis Xc of the carrier body portion 31, or the central axis of the scraping portion 35 may be The flange portion 32 may be fixed to the carrier body portion 31 such that the flange portion 32 has an eccentric positional relationship with respect to the rotation axis Xc of the carrier body portion 31. In this embodiment, the flange portion 32 is a separate member from the carrier body portion 31, and is integrated with the carrier body portion 31 by welding. FIG. 4 is an enlarged view of the upper part of the drive transmission device 10. As shown in FIG. FIG. 5 is an enlarged view of the lower part of the drive transmission device 10. As shown in FIG.
掻き上げ部35は、リングギヤ25に対して軸方向Xの一方側に配置されている。本実施形態では、軸方向Xにおける、リングギヤ25に対して、掻き上げ部35が配置されている側が軸方向第1側X1となり、その反対側が軸方向第2側X2となっている。図示の例では、掻き上げ部35とリングギヤ25とは、間に他の部材が挟まれていない状態で、軸方向Xに隣り合うように配置されている。なお、掻き上げ部35とリングギヤ25との間には他の部材、例えば、ケース50に設けられたリブや、別の部材が配置されていても良い。
The scraping part 35 is arranged on one side of the ring gear 25 in the axial direction X. In this embodiment, with respect to the ring gear 25 in the axial direction X, the side on which the scraping portion 35 is arranged is the first axial side X1, and the opposite side is the second axial side X2. In the illustrated example, the scraping portion 35 and the ring gear 25 are arranged adjacent to each other in the axial direction X without any other member being sandwiched between them. Note that another member, such as a rib provided on the case 50 or another member, may be arranged between the scraping part 35 and the ring gear 25.
図3に示すように、掻き上げ部35の回転軌跡の下端Tfは、ピニオン22の公転軌跡の下端Tpよりも下側Z2に配置されている。図示の例では、下端Tfが掻き上げ部35の回転軌跡における外縁Cfの下端として示され、下端Tpがピニオン22の公転軌跡における歯先円Cpの下端として示されている。本実施形態では、上記のとおり、掻き上げ部35は、キャリヤ本体部31に対して径方向Rの外側に突出したフランジ部32の外周面に形成されている。よって、掻き上げ部35はキャリヤ30の最外周縁部に設けられている。なお、掻き上げ部35は、当該掻き上げ部35の回転軌跡の下端Tfがピニオン22の公転軌跡の下端Tpよりも下側Z2に配置されているのであれば、キャリヤ30の最外周縁部に設けられている必要はなく、例えば、キャリヤ30の最外周縁部よりも内側に配置された部分の外周部に設けられていても良い。
As shown in FIG. 3, the lower end Tf of the rotational trajectory of the scraping unit 35 is located below the lower end Tp of the revolutional trajectory of the pinion 22 Z2. In the illustrated example, the lower end Tf is shown as the lower end of the outer edge Cf on the rotation locus of the rake-up portion 35, and the lower end Tp is shown as the lower end of the tip circle Cp on the revolution locus of the pinion 22. In this embodiment, as described above, the scraping portion 35 is formed on the outer circumferential surface of the flange portion 32 that protrudes outward in the radial direction R with respect to the carrier body portion 31. Therefore, the scraping portion 35 is provided at the outermost peripheral edge of the carrier 30. Note that if the lower end Tf of the rotation locus of the rake-up portion 35 is located below the lower end Tp of the revolution locus of the pinion 22, the scraping portion 35 is located at the outermost peripheral edge of the carrier 30. It does not need to be provided, and may be provided, for example, on the outer periphery of a portion of the carrier 30 that is located inside the outermost periphery.
本実施形態では、入力軸15は、遊星歯車機構20のサンギヤ21と一体的に形成されている。出力軸16は、キャリヤ30と一体的に回転するように連結されている。図示の例では、出力軸16は、軸状に形成された出力軸本体部16aと、フランジ状に形成された出力軸フランジ部16bとを備えている。本例では、出力軸フランジ部16bは、出力軸本体部16aの軸方向第2側X2の端部から、径方向Rの外側に突出するように形成されている。また、出力軸フランジ部16bは、円盤状に形成されている。そして、出力軸フランジ部16bの外周面に、キャリヤ30と連結するための第1スプライン係合部16cが形成されている。また、本実施形態では、キャリヤ30におけるフランジ部32の内周面に、第1スプライン係合部16cと係合する第2スプライン係合部32aが形成されている。
In this embodiment, the input shaft 15 is integrally formed with the sun gear 21 of the planetary gear mechanism 20. The output shaft 16 is connected to the carrier 30 so as to rotate together with the carrier 30. In the illustrated example, the output shaft 16 includes an output shaft main body portion 16a formed in the shape of a shaft, and an output shaft flange portion 16b formed in the shape of a flange. In this example, the output shaft flange portion 16b is formed to protrude outward in the radial direction R from the end of the output shaft main body portion 16a on the second axial side X2. Further, the output shaft flange portion 16b is formed into a disk shape. A first spline engagement portion 16c for connecting to the carrier 30 is formed on the outer peripheral surface of the output shaft flange portion 16b. Further, in this embodiment, a second spline engagement portion 32a that engages with the first spline engagement portion 16c is formed on the inner circumferential surface of the flange portion 32 of the carrier 30.
上記のとおり、本実施形態では、フランジ部32は、キャリヤ本体部31に対して軸方向第1側X1に突出するように形成されている。フランジ部32の当該突出部分の内周面に、第2スプライン係合部32aが形成されている。図4及び図5に示す例では、第2スプライン係合部32aにスナップリング36が係止されている。このスナップリング36は、第1スプライン係合部16cに対して軸方向第1側X1に配置され、出力軸フランジ部16bは、スナップリング36とキャリヤ本体部31との軸方向Xの間に挟まれて配置されている。これにより、本実施形態では、キャリヤ本体部31とフランジ部32と出力軸フランジ部16bとが一体化されている。
As described above, in this embodiment, the flange portion 32 is formed to protrude toward the first axial side X1 with respect to the carrier body portion 31. A second spline engagement portion 32 a is formed on the inner peripheral surface of the protruding portion of the flange portion 32 . In the example shown in FIGS. 4 and 5, a snap ring 36 is locked to the second spline engagement portion 32a. The snap ring 36 is disposed on the first axial side X1 with respect to the first spline engagement portion 16c, and the output shaft flange portion 16b is sandwiched between the snap ring 36 and the carrier body portion 31 in the axial direction X. It is arranged according to the following. As a result, in this embodiment, the carrier main body portion 31, the flange portion 32, and the output shaft flange portion 16b are integrated.
本実施形態では、パーキングギヤ40が、キャリヤ30及びリングギヤ25に対して軸方向第2側X2に配置されている。本例では、パーキングギヤ40は入力軸15と一体的に回転するように入力軸15に固定されている。具体的には、パーキングギヤ40は、入力軸15とスプライン係合されることにより、一体的に回転するように連結されている。
In this embodiment, the parking gear 40 is arranged on the second axial side X2 with respect to the carrier 30 and the ring gear 25. In this example, the parking gear 40 is fixed to the input shaft 15 so as to rotate integrally with the input shaft 15. Specifically, the parking gear 40 is connected to the input shaft 15 by spline engagement so as to rotate together with the input shaft 15.
ケース50には、掻き上げ部35により掻き上げられた油を潤滑必要箇所70へ流す油供給経路Rtが形成されている。油供給経路Rtは、ケース50の内面に設けられた溝やリブ、ケース50に形成された貫通孔、ケース50の内面そのもの、或いは、これらの一部又は全部の組み合わせにより構成されると良い。本実施形態では、後述の対向内周面53、上側凹部54、油受け面54a、側壁面55、油溝57、突出部58、突出外周面58a、突出端面58b、第1連通油路61から第4連通油路64等が油供給経路Rtとして機能している。
An oil supply path Rt is formed in the case 50 to flow the oil scraped up by the scraping portion 35 to the location 70 requiring lubrication. The oil supply path Rt may be configured by a groove or rib provided on the inner surface of the case 50, a through hole formed in the case 50, the inner surface of the case 50 itself, or a combination of some or all of these. In this embodiment, from the opposing inner circumferential surface 53, the upper recess 54, the oil receiving surface 54a, the side wall surface 55, the oil groove 57, the protruding part 58, the protruding outer circumferential surface 58a, the protruding end surface 58b, and the first communicating oil passage 61, which will be described later. The fourth communicating oil passage 64 and the like function as an oil supply route Rt.
本実施形態では、潤滑必要箇所70には、入力軸15をケース50に対して回転自在に支持する一対の入力軸受71である第1入力軸受71a及び第2入力軸受71bと、出力軸16をケース50に対して回転自在に支持する出力軸受72である第1出力軸受72a及び第2出力軸受72bと、が含まれる。また、本実施形態では、潤滑必要箇所70には、ピニオン22をキャリヤ30に対して回転自在に支持するピニオン軸受73が含まれる。また、ピニオン22とリングギヤ25との噛み合い部や、ピニオン22とサンギヤ21との噛み合い部等が含まれていても良い。また、本実施形態では、入力軸受71及び出力軸受72も潤滑必要箇所70に含まれる。
In this embodiment, the lubrication required portion 70 includes a first input bearing 71a and a second input bearing 71b, which are a pair of input bearings 71 that rotatably support the input shaft 15 with respect to the case 50, and the output shaft 16. A first output bearing 72a and a second output bearing 72b, which are output bearings 72 rotatably supported with respect to the case 50, are included. Furthermore, in this embodiment, the lubrication-requiring locations 70 include a pinion bearing 73 that rotatably supports the pinion 22 with respect to the carrier 30. Further, a meshing portion between the pinion 22 and the ring gear 25, a meshing portion between the pinion 22 and the sun gear 21, etc. may be included. Further, in this embodiment, the input bearing 71 and the output bearing 72 are also included in the locations 70 requiring lubrication.
図2に示すように、本実施形態では、ケース50は互いにボルト42で液密に締結された第1ケース部50aと第2ケース部50bとを有している。ケース50の内部空間は液密状態の空間であり、ケース50の下部が油を貯留するオイル貯留部となっている。本実施形態では、ケース50内の油、すなわち、オイル貯留部の油が掻き上げ部35により掻き上げられて、油供給経路Rtを通り潤滑必要箇所70に供給される。なお、ケース50は非回転部材である。
As shown in FIG. 2, in this embodiment, the case 50 includes a first case part 50a and a second case part 50b that are liquid-tightly fastened to each other with bolts 42. The internal space of the case 50 is a liquid-tight space, and the lower part of the case 50 serves as an oil storage section for storing oil. In this embodiment, the oil in the case 50, that is, the oil in the oil storage section, is scooped up by the scooping section 35 and is supplied to the lubrication required location 70 through the oil supply path Rt. Note that the case 50 is a non-rotating member.
好適には、車両11の定常走行状態でのケース50内の油面高さL1が、ピニオン22の公転軌跡の下端Tpよりも下側Z2であって掻き上げ部35の回転軌跡の下端Tfよりも上側Z1になるように油量が設定される。ここで、定常走行状態とは、車両11が走行することにより、ケース50内の油面高さL1が安定する程度の速度で駆動伝達装置10の内部の各回転部材が回転している状態である。このような設定にした場合、ピニオン22による油の撹拌を少なく抑えることができる。また、車両11の長期停止状態でのケース50内の油面高さL2を、ピニオン軸受73以上になるように設定すると好適である。ここで、長期停止状態とは、ケース50内の油のほとんどがオイル貯留部に落ちてケース50内の油面高さL1が最も高くなっている状態である。このような設定にした場合、長期間停止した状態となっていた場合であってもピニオン軸受73に油が供給された状態とすることができる。従って、長期間停止した状態となっていた車両11が走行を開始した際に、キャリヤ30に複数設けられたピニオン軸受73が回転方向に順に油に浸かることができ、ピニオン軸受73に油が供給された状態とすることができる。
Preferably, the oil level height L1 in the case 50 when the vehicle 11 is in a steady running state is lower than the lower end Tp of the revolution locus of the pinion 22 and lower than the lower end Tf of the rotation locus of the scraping part 35. The oil amount is set so that the upper side Z1 is also reached. Here, the steady running state is a state in which each rotating member inside the drive transmission device 10 is rotating at a speed that stabilizes the oil level height L1 in the case 50 as the vehicle 11 runs. be. With such a setting, the stirring of oil by the pinion 22 can be suppressed to a small level. Further, it is preferable that the oil level height L2 in the case 50 when the vehicle 11 is stopped for a long period of time is set to be equal to or higher than the pinion bearing 73. Here, the long-term stopped state is a state in which most of the oil in the case 50 falls into the oil storage part and the oil level height L1 in the case 50 is the highest. With such a setting, oil can be supplied to the pinion bearing 73 even if the engine has been stopped for a long period of time. Therefore, when the vehicle 11 starts running after being stopped for a long time, the plurality of pinion bearings 73 provided on the carrier 30 can be immersed in oil in order in the rotational direction, and oil is supplied to the pinion bearings 73. It can be in a state where
図3に示すように、本実施形態では、ケース50は、掻き上げ部35に対して径方向Rの外側から対向する対向内周面53を備えている。この対向内周面53は、回転軸心Xcよりも上側Z1に配置され、軸方向Xに沿う軸方向視で掻き上げ部35の回転軌跡における外縁Cfの接線に交差するように配置された油受け面54aを備えている。このような油受け面54aを備えることにより、掻き上げ部35により掻き上げた油を掻き上げ部35よりも上側Z1で受け止め、そこから重力を利用して油供給経路Rtに沿って油を流すことができる。図示の例では、油受け面54aは外縁Cfの接線に直交するように配置されている。より具体的には、油受け面54aは外縁Cfの上端における接線に直交するように配置されている。本実施形態では、対向内周面53に、掻き上げ部35の回転軌跡の上端領域に対向する部分が他の部分に比べて上側Z1に窪んだ上側凹部54が形成され、上側凹部54の周方向側面が油受け面54aとなっている。好適には上側凹部54の周方向Cの両側面に油受け面54aが設けられるが、周方向Cの一方側にのみ、例えば、前進回転時に掻き上げられた油が当たる向きの油受け面54aのみが設けられていても良い。
As shown in FIG. 3, in this embodiment, the case 50 includes an opposing inner circumferential surface 53 that faces the scraping portion 35 from the outside in the radial direction R. This opposing inner circumferential surface 53 is arranged above the rotational axis Xc at an upper side Z1, and is arranged so as to intersect with a tangent to the outer edge Cf of the rotation locus of the scraping part 35 when viewed in the axial direction along the axial direction X. It has a receiving surface 54a. By providing such an oil receiving surface 54a, the oil scraped up by the scraping part 35 is received at the upper side Z1 of the scraping part 35, and the oil is flowed from there along the oil supply route Rt using gravity. be able to. In the illustrated example, the oil receiving surface 54a is arranged to be perpendicular to the tangent to the outer edge Cf. More specifically, the oil receiving surface 54a is arranged to be perpendicular to the tangent at the upper end of the outer edge Cf. In this embodiment, an upper recess 54 is formed in the opposing inner circumferential surface 53 in which a portion facing the upper end region of the rotation locus of the scraping portion 35 is recessed upward Z1 compared to other portions, and the periphery of the upper recess 54 is recessed. The side surface in the direction serves as an oil receiving surface 54a. Preferably, oil receiving surfaces 54a are provided on both sides of the upper recess 54 in the circumferential direction C, but only on one side in the circumferential direction C, for example, the oil receiving surface 54a is provided in the direction in which the oil scraped up during forward rotation hits. Only one may be provided.
図4に示すように、本実施形態では、ケース50は、キャリヤ30に対して軸方向第1側X1に配置され、軸方向第2側X2を向く側壁面55を備えている。この側壁面55には、潤滑必要箇所70に連通する油溝57が形成されている。油溝57は、軸方向第2側X2に向けて開口している。このようにすれば、掻き上げ部35により掻き上げた油を、効率的に油溝57に導くことができ、当該油溝57を通じて潤滑必要箇所70に多くの油を供給し易い。本実施形態では、油受け面54aと油溝57とが接続されて、潤滑必要箇所70に連通する油供給経路Rtを形成している。また、本例では、油溝57は、側壁面55に対して軸方向第1側X1に窪んだ凹溝状に形成されている。
As shown in FIG. 4, in this embodiment, the case 50 is disposed on the first axial side X1 with respect to the carrier 30, and includes a side wall surface 55 facing the second axial side X2. An oil groove 57 is formed in this side wall surface 55 and communicates with a location 70 requiring lubrication. The oil groove 57 is open toward the second axial side X2. In this way, the oil scraped up by the scraping part 35 can be efficiently guided to the oil groove 57, and a large amount of oil can be easily supplied to the parts 70 requiring lubrication through the oil groove 57. In this embodiment, the oil receiving surface 54a and the oil groove 57 are connected to form an oil supply path Rt communicating with the location 70 requiring lubrication. Further, in this example, the oil groove 57 is formed in the shape of a concave groove that is recessed toward the first axial side X1 with respect to the side wall surface 55.
図5に示すように、本実施形態では、駆動伝達装置10は、油受け部80を更に備えている。油受け部80は、キャリヤ30に固定されている。また、油受け部80は、掻き上げ部35よりも径方向Rの内側に配置されて径方向Rの内側に向けて開口するように形成されている。また、本実施形態では、掻き上げ部35は、リングギヤ25と側壁面55との軸方向Xの間に配置され、油受け部80は、キャリヤ30と側壁面55との軸方向Xの間に配置されている。油受け部80は、キャリヤ30に直接固定されていても良く、一体的に回転する部材を挟んで間接的に固定されていても良い。本実施形態では、油受け部80は、キャリヤ30と一体的に回転する出力軸フランジ部16bに固定されている。また、本実施形態では、油受け部80は、全周に亘って連続的に形成されている。より具体的には、油受け部80は、円環状に形成されていると共に、図4及び図5に示されているように、断面形状が、径方向Rの内側に向かうに従って軸方向第1側X1へ向かうように傾斜した形状となっている。
As shown in FIG. 5, in this embodiment, the drive transmission device 10 further includes an oil receiver 80. The oil receiver 80 is fixed to the carrier 30. Further, the oil receiving portion 80 is disposed on the inner side in the radial direction R than the scraping portion 35 and is formed to open toward the inner side in the radial direction R. Further, in this embodiment, the scraping part 35 is arranged between the ring gear 25 and the side wall surface 55 in the axial direction X, and the oil receiving part 80 is arranged between the carrier 30 and the side wall surface 55 in the axial direction X. It is located. The oil receiving portion 80 may be directly fixed to the carrier 30, or may be indirectly fixed to the carrier 30 with an integrally rotating member interposed therebetween. In this embodiment, the oil receiver 80 is fixed to the output shaft flange 16b that rotates integrally with the carrier 30. Furthermore, in this embodiment, the oil receiving portion 80 is formed continuously over the entire circumference. More specifically, the oil receiving portion 80 is formed in an annular shape, and as shown in FIGS. 4 and 5, the cross-sectional shape becomes axially first as it goes inward in the radial direction It has a shape that is inclined toward the side X1.
本実施形態では、ケース50は、油受け部80よりも径方向Rの内側において、側壁面55から軸方向第2側X2に突出するように形成され、径方向Rに沿う径方向視で油受け部80と重複するように配置された突出部58を更に備えている。本実施形態では、突出部58は、側壁面55よりも軸方向第2側X2に突出するように形成されている。ここで、2つの部材の配置に関して、「特定方向視で重複する」とは、その視線方向に平行な仮想直線を当該仮想直線に直交する各方向に移動させた場合に、当該仮想直線が2つの部材の双方に交わる領域が存在することを指す。
In this embodiment, the case 50 is formed so as to protrude from the side wall surface 55 toward the second axial side X2 on the inner side of the oil receiving portion 80 in the radial direction R, and the case 50 is formed so as to protrude from the side wall surface 55 toward the second axial side X2. It further includes a protrusion 58 arranged to overlap the receiving part 80. In this embodiment, the protruding portion 58 is formed to protrude from the side wall surface 55 toward the second axial side X2. Here, regarding the arrangement of two members, "overlapping when viewed in a specific direction" means that when a virtual straight line parallel to the line of sight is moved in each direction orthogonal to the virtual straight line, the virtual straight line is two Refers to the existence of an area that intersects both of the two members.
本実施形態では、突出部58は、径方向Rの外側を向く突出外周面58aと、軸方向第2側X2を向く突出部58の端面である突出端面58bとを備えている。図示の例では、ケース50が備える第2筒状部52における側壁面55よりも軸方向第2側X2の部分が突出部58となっている。また、突出外周面58aにおける下側Z2を向く部分であって突出端面58bに対して軸方向第1側X1に隣接する部分には、下側Z2に開口する油切溝59が設けられている。
In the present embodiment, the protruding portion 58 includes a protruding outer circumferential surface 58a facing outward in the radial direction R, and a protruding end surface 58b, which is an end surface of the protruding portion 58 facing the second axial side X2. In the illustrated example, a portion of the second cylindrical portion 52 of the case 50 that is closer to the second axial side X2 than the side wall surface 55 is the protruding portion 58 . Further, an oil cutting groove 59 that opens toward the lower side Z2 is provided in a portion of the protruding outer circumferential surface 58a facing the lower side Z2 and adjacent to the first axial side X1 with respect to the protruding end surface 58b. .
また、本実施形態では、キャリヤ30には、油受け部80とピニオン軸受73とを連通するキャリヤ内油路38が形成されている。従って、掻き上げ部35により掻き上げられた油は、側壁面55或いは油溝57に沿って下側Z2へ流れて突出外周面58aに到達する。突出外周面58aに到達した油は、当該突出外周面58aに沿って周方向Cに下側Z2へ向かって流れると共に、突出端面58bに沿って下側Z2へ流れる。そして、突出外周面58a又は突出端面58bから落下した油が油受け部80により受け止められる。なお、突出外周面58aに設けられた油切溝59は、突出外周面58a及び突出端面58bの下端部に到達した油を、突出部58よりも下側Z2の側壁面55の側へ流れ難くする機能を果たす。油受け部80に受け止められた油は、当該油受け部80の形状によってキャリヤ内油路38に導かれ、当該キャリヤ内油路38を通ってピニオン軸受73に供給される。
Furthermore, in this embodiment, the carrier 30 is formed with an in-carrier oil passage 38 that communicates the oil receiver 80 and the pinion bearing 73. Therefore, the oil scraped up by the scraping part 35 flows toward the lower side Z2 along the side wall surface 55 or the oil groove 57 and reaches the protruding outer circumferential surface 58a. The oil that has reached the protruding outer circumferential surface 58a flows toward the lower side Z2 in the circumferential direction C along the protruding outer circumferential surface 58a, and also flows toward the lower side Z2 along the protruding end surface 58b. The oil falling from the protruding outer circumferential surface 58a or the protruding end surface 58b is received by the oil receiving portion 80. Note that the oil cutting grooves 59 provided on the protruding outer circumferential surface 58a prevent the oil that has reached the lower ends of the protruding outer circumferential surface 58a and the protruding end surface 58b from flowing toward the side wall surface 55 on the lower side Z2 than the protruding portion 58. fulfill the function of The oil received by the oil receiver 80 is guided to the carrier oil passage 38 by the shape of the oil receiver 80 and is supplied to the pinion bearing 73 through the carrier oil passage 38 .
本実施形態では、キャリヤ内油路38は、ピニオンシャフト23内に形成された空間23aと、当該空間23aを油受け部80の側に連通させる軸方向貫通孔38a、及び、空間23aとピニオンシャフト23の外周面とを径方向Rに連通する径方向貫通孔38bを備えている。径方向貫通孔38bから排出された油は、ピニオン軸受73に供給される。軸方向貫通孔38aは、キャリヤ本体部31及び出力軸フランジ部16bを軸方向Xに貫通している。
In this embodiment, the carrier oil passage 38 includes a space 23a formed in the pinion shaft 23, an axial through hole 38a that communicates the space 23a with the oil receiver 80, and a space 23a and the pinion shaft. A radial through hole 38b that communicates with the outer circumferential surface of 23 in the radial direction R is provided. The oil discharged from the radial through hole 38b is supplied to the pinion bearing 73. The axial through hole 38a passes through the carrier body portion 31 and the output shaft flange portion 16b in the axial direction X.
本実施形態では、ケース50は、入力軸受71を径方向Rの外側から支持する筒状の第1筒状部51と、出力軸受72を径方向Rの外側から支持する筒状の第2筒状部52と、を備えている。第1筒状部51には、第1筒状部51の外周面における上側Z1を向く部分と入力軸受71を支持する内周面とを連通する第1連通油路61が形成されている。また、第2筒状部52には、第2筒状部52の外周面における上側Z1を向く部分と出力軸受72を支持する内周面とを連通する第2連通油路62が形成されている。
In the present embodiment, the case 50 includes a first cylindrical portion 51 that supports the input bearing 71 from the outside in the radial direction R, and a second cylindrical portion that supports the output bearing 72 from the outside in the radial direction R. A shaped portion 52 is provided. A first communication oil passage 61 is formed in the first cylindrical portion 51 . The first communicating oil passage 61 communicates between a portion of the outer circumferential surface of the first cylindrical portion 51 facing upward Z1 and an inner circumferential surface that supports the input bearing 71 . Further, a second communication oil passage 62 is formed in the second cylindrical portion 52, which communicates between the portion of the outer circumferential surface of the second cylindrical portion 52 facing the upper side Z1 and the inner circumferential surface that supports the output bearing 72. There is.
このようにすれば、掻き上げ部35により掻き上げられ第1筒状部51の外周面における上側Z1を向く部分に到達した油の一部が、第1連通油路61に入る。そして、当該第1連通油路61に入った油は入力軸受71に到達することになる。これにより、入力軸受71を潤滑することができる。また、掻き上げ部35により掻き上げられ、上記のように側壁面55或いは油溝57に沿って第2筒状部52の外周面(すなわち突出外周面58a)における上側Z1を向く部分に到達した油の一部が、第2連通油路62に入る。そして、当該第2連通油路62に入った油は出力軸受72に到達することになる。これにより、出力軸受72を潤滑することができる。これにより、例えば、入力軸15及び出力軸16の内部に油路を設けることなく、各軸受を潤滑することができる。なお、第1筒状部51に到達する油の油供給経路Rtは、ケース50の内面を伝う経路であっても良く、ケース50内の図示しない貫通孔や油溝等を通る経路であっても良い。また、パーキングギヤ40により掻き上げられた油が第1連通油路61を介して入力軸受71に到達するものであっても良い。
In this way, a part of the oil that has been scraped up by the scraping part 35 and has reached the part of the outer circumferential surface of the first cylindrical part 51 facing the upper side Z1 enters the first communicating oil passage 61. The oil that has entered the first communication oil passage 61 then reaches the input bearing 71. Thereby, the input bearing 71 can be lubricated. Further, the scraped up part 35 reaches the part of the outer circumferential surface (i.e., the protruding outer circumferential surface 58a) of the second cylindrical part 52 facing the upper side Z1 along the side wall surface 55 or the oil groove 57 as described above. A portion of the oil enters the second communication oil passage 62. The oil that has entered the second communicating oil passage 62 then reaches the output bearing 72. Thereby, the output bearing 72 can be lubricated. Thereby, each bearing can be lubricated, for example, without providing oil passages inside the input shaft 15 and the output shaft 16. Note that the oil supply path Rt for the oil that reaches the first cylindrical portion 51 may be a path that runs along the inner surface of the case 50, or a path that passes through a through hole or an oil groove (not shown) in the case 50. Also good. Further, the oil scooped up by the parking gear 40 may reach the input bearing 71 via the first communication oil passage 61.
本実施形態では、第1筒状部51には、第1筒状部51の外周面における下側Z2を向く部分と入力軸受71を支持する内周面とを連通する第3連通油路63が形成されている。また、第2筒状部52には、当該第2筒状部52の外周面における下側Z2を向く部分と出力軸受72を支持する内周面とを連通する第4連通油路64が形成されている。第1連通油路61と第3連通油路63とは、第1筒状部51の内周面において、第2入力軸受71bを挟んで互いに軸方向Xの反対側に開口するように設けられている。また、第2連通油路62と第4連通油路64とは、第2筒状部52の内周面において、第1出力軸受72aを挟んで互いに軸方向Xの反対側に開口するように設けられている。
In the present embodiment, the first cylindrical portion 51 includes a third communication oil passage 63 that communicates between the portion of the outer circumferential surface of the first cylindrical portion 51 facing the lower side Z2 and the inner circumferential surface that supports the input bearing 71. is formed. Further, a fourth communication oil passage 64 is formed in the second cylindrical portion 52, which communicates the portion of the outer circumferential surface of the second cylindrical portion 52 facing the lower side Z2 with the inner circumferential surface that supports the output bearing 72. has been done. The first communication oil passage 61 and the third communication oil passage 63 are provided on the inner peripheral surface of the first cylindrical portion 51 so as to open on opposite sides in the axial direction X with the second input bearing 71b interposed therebetween. ing. Further, the second communication oil passage 62 and the fourth communication oil passage 64 are configured to open on opposite sides in the axial direction It is provided.
このようにすれば、第1連通油路61から供給されて第2入力軸受71bを潤滑した後の油を、第3連通油路63を介して第1筒状部51よりも下側Z2に排出することができる。同様に、第2連通油路62から供給されて第1出力軸受72aを潤滑した後の油を、第4連通油路64を介して第2筒状部52よりも下側Z2に排出することができる。従って、第2入力軸受71b及び第1出力軸受72aを潤滑した後の油を、適切に排出してケース50内で循環させることができる。なお、第1連通油路61から供給されて第1入力軸受71aを潤滑した後の油は、第1筒状部51の軸方向第1側X1の端部から排出される。同様に、第2連通油路62から供給されて第2出力軸受72bを潤滑した後の油は、第2筒状部52の軸方向第2側X2の端部から排出される。
In this way, the oil supplied from the first communication oil passage 61 to lubricate the second input bearing 71b is sent to the lower side Z2 than the first cylindrical part 51 via the third communication oil passage 63. Can be discharged. Similarly, the oil supplied from the second communication oil passage 62 and after lubricating the first output bearing 72a is discharged to the lower side Z2 than the second cylindrical part 52 via the fourth communication oil passage 64. I can do it. Therefore, the oil after lubricating the second input bearing 71b and the first output bearing 72a can be appropriately discharged and circulated within the case 50. Note that the oil supplied from the first communicating oil passage 61 to lubricate the first input bearing 71a is discharged from the end of the first axially first side X1 of the first cylindrical portion 51. Similarly, the oil supplied from the second communicating oil passage 62 and lubricating the second output bearing 72b is discharged from the end of the second cylindrical portion 52 on the second axial side X2.
本実施形態では、第1筒状部51の内周面と入力軸15の外周面の間には、ケース50の外への油の漏出を防ぐための入力側オイルシール81が配置されている。また、第2筒状部52の内周面と出力軸16の外周面の間には、ケース50の外への油の漏出を防ぐための出力側オイルシール82が配置されている。
In this embodiment, an input side oil seal 81 is arranged between the inner circumferential surface of the first cylindrical portion 51 and the outer circumferential surface of the input shaft 15 to prevent oil from leaking out of the case 50. . Furthermore, an output side oil seal 82 is arranged between the inner circumferential surface of the second cylindrical portion 52 and the outer circumferential surface of the output shaft 16 to prevent oil from leaking out of the case 50.
本実施形態では、掻き上げ部35は、リングギヤ25に対して軸方向Xの一方側に配置され、掻き上げ部35の回転軌跡の下端Tfが、ピニオン22の公転軌跡の下端Tpよりも下側Z2に配置され、ケース50に、掻き上げ部35により掻き上げられた油を潤滑必要箇所70へ流す油供給経路Rtが形成されている。
In this embodiment, the scraping part 35 is arranged on one side of the ring gear 25 in the axial direction An oil supply path Rt is formed in the case 50 and flows the oil scraped up by the scraping portion 35 to the location 70 requiring lubrication.
本実施形態では、対向内周面53は、回転軸心Xcよりも上側Z1に配置され、軸方向Xに沿う軸方向視で掻き上げ部35の回転軌跡における外縁Cfの接線に交差するように配置された油受け面54aを備える。
In the present embodiment, the opposing inner circumferential surface 53 is disposed above the rotation axis Xc at an upper side Z1, and is arranged so as to intersect with a tangent to the outer edge Cf of the rotation locus of the scraping part 35 when viewed in the axial direction along the axial direction X. An oil receiving surface 54a is provided.
本実施形態では、潤滑必要箇所70には、ピニオン22をキャリヤ30に対して回転自在に支持するピニオン軸受73が含まれ、キャリヤ30には、油受け部80とピニオン軸受73とを連通するキャリヤ内油路38が形成されている。
In this embodiment, the parts 70 requiring lubrication include a pinion bearing 73 that rotatably supports the pinion 22 with respect to the carrier 30, and the carrier 30 includes a carrier that communicates the oil receiver 80 with the pinion bearing 73. An inner oil passage 38 is formed.
本実施形態では、油溝57は、軸方向第2側X2に向けて開口し、掻き上げ部35は、キャリヤ30に設けられたフランジ部32の外周面に形成された外歯のはすばギヤ状に形成され、車両11の前進中の掻き上げ部35の回転によって、油を軸方向第1側X1に向けて飛ばすような向きに形成されている。
In this embodiment, the oil groove 57 opens toward the second axial side It is formed in a gear shape and is oriented such that oil is blown toward the first side X1 in the axial direction by rotation of the scraping portion 35 while the vehicle 11 is moving forward.
〔第2の実施形態〕
以下では、第2の実施形態に係る駆動伝達装置10について図6を参照して説明する。本実施形態では、駆動伝達装置10がオイルポンプ110を備えている点、第1筒状部51に第3連通油路63が形成されていない点、及び、第2筒状部52に第4連通油路64が形成されていない点等で第1の実施形態と異なっている。以下では、上記第1の実施形態との相違点を中心として説明する。なお、特に説明しない点については、上記第1の実施形態と同様とする。 [Second embodiment]
Adrive transmission device 10 according to a second embodiment will be described below with reference to FIG. 6. In this embodiment, the drive transmission device 10 includes an oil pump 110, the third communicating oil passage 63 is not formed in the first cylindrical part 51, and the fourth communicating oil passage 63 is not formed in the second cylindrical part 52. This embodiment differs from the first embodiment in that a communicating oil passage 64 is not formed. Below, the explanation will focus on the differences from the first embodiment. Note that points not particularly described are the same as those in the first embodiment.
以下では、第2の実施形態に係る駆動伝達装置10について図6を参照して説明する。本実施形態では、駆動伝達装置10がオイルポンプ110を備えている点、第1筒状部51に第3連通油路63が形成されていない点、及び、第2筒状部52に第4連通油路64が形成されていない点等で第1の実施形態と異なっている。以下では、上記第1の実施形態との相違点を中心として説明する。なお、特に説明しない点については、上記第1の実施形態と同様とする。 [Second embodiment]
A
本実施形態では、駆動伝達装置10は、ケース50内の油を吸引し、油供給経路Rtに油を供給するオイルポンプ110を備えている。オイルポンプ110は、第1ケース部50a及び第2ケース部50bにより支持されている。オイルポンプ110はオイルクーラ(不図示)を介して油供給経路Rtに油を供給することが好ましい。また、オイルポンプ110がケース50内の油を吸引する吸引口(不図示)は、車両11の定常走行状態でのケース50内の油面高さL1よりも下側Z2に配置されていることが好ましい。
In the present embodiment, the drive transmission device 10 includes an oil pump 110 that sucks oil in the case 50 and supplies oil to the oil supply path Rt. The oil pump 110 is supported by a first case part 50a and a second case part 50b. It is preferable that the oil pump 110 supplies oil to the oil supply path Rt via an oil cooler (not shown). Further, a suction port (not shown) through which the oil pump 110 sucks oil in the case 50 is arranged at a lower side Z2 than the oil level height L1 in the case 50 when the vehicle 11 is in a steady running state. is preferred.
本実施形態では、回転軸心Xc回りに回動するパーキングポール41が、パーキングギヤ40と選択的に係合する。また、本実施形態では、径方向Rに沿う径方向視でオイルポンプ110が、パーキングギヤ40、パーキングポール41、又は、パーキングギヤ40及びパーキングポール41と、重複するように配置されている。
In this embodiment, the parking pole 41 that rotates around the rotation axis Xc selectively engages with the parking gear 40. Furthermore, in this embodiment, the oil pump 110 is arranged so as to overlap the parking gear 40, the parking pole 41, or the parking gear 40 and the parking pole 41 when viewed in the radial direction R.
本実施形態では、オイルポンプ110は、入力軸15又は出力軸16の回転に伴って駆動される機械式オイルポンプである。また、本実施形態では、駆動伝達装置10は、キャリヤ30と一体的に回転してオイルポンプ110を駆動するポンプ駆動ギヤ111を備えている。本例では、ポンプ駆動ギヤ111は、キャリヤ本体部31に溶接等により固定されている。また、ポンプ駆動ギヤ111は、キャリヤ本体部31とパーキングギヤ40との軸方向Xの間に挟まれて配置されている。
In this embodiment, the oil pump 110 is a mechanical oil pump that is driven as the input shaft 15 or the output shaft 16 rotates. Further, in this embodiment, the drive transmission device 10 includes a pump drive gear 111 that rotates integrally with the carrier 30 and drives the oil pump 110. In this example, the pump drive gear 111 is fixed to the carrier body 31 by welding or the like. Further, the pump drive gear 111 is disposed between the carrier body 31 and the parking gear 40 in the axial direction X.
本実施形態では、オイルポンプ110は、車両11の前進中に油供給経路Rtに油を供給するように構成されている。また、掻き上げ部35は、キャリヤ30に設けられたフランジ部32の外周面に形成された外歯のはすば歯車状に形成され、車両11の後進中の掻き上げ部35の回転によって、油を軸方向第1側X1に向けて飛ばすような向きに形成されている。このようにすれば、車両11の前進中にオイルポンプ110により油供給経路Rtに油を多く供給できるとともに、車両11の後進中にも、掻き上げ部35により掻き上げた油を油溝57から油供給経路Rtに油を多く供給できる。
In this embodiment, the oil pump 110 is configured to supply oil to the oil supply path Rt while the vehicle 11 is moving forward. Further, the scraping portion 35 is formed in the shape of an external helical gear formed on the outer peripheral surface of the flange portion 32 provided on the carrier 30, and is rotated by the rotation of the scraping portion 35 while the vehicle 11 is moving backward. It is formed in such a direction that the oil is blown toward the first side X1 in the axial direction. In this way, while the vehicle 11 is moving forward, the oil pump 110 can supply a large amount of oil to the oil supply path Rt, and even while the vehicle 11 is moving backward, the oil scraped up by the scooping part 35 can be removed from the oil groove 57. A large amount of oil can be supplied to the oil supply path Rt.
本実施形態では、入力軸15は、サンギヤ21に対し軸方向Xの両側に配置された一対の入力軸受71により支持されている。また、出力軸16は、複列式の出力軸受72により支持されている。また、出力軸受72の外輪は、係止部材78によりケース50に固定されている。係止部材78は、出力軸受72の軸方向第2側X2に配置され、出力軸受72の軸方向第1側X1のケース50の壁面と出力軸受72の外輪を挟持する。
In this embodiment, the input shaft 15 is supported by a pair of input bearings 71 arranged on both sides of the sun gear 21 in the axial direction X. Further, the output shaft 16 is supported by a double-row output bearing 72. Further, the outer ring of the output bearing 72 is fixed to the case 50 by a locking member 78. The locking member 78 is disposed on the second axial side X2 of the output bearing 72 and holds the outer ring of the output bearing 72 between the wall surface of the case 50 on the first axial side X1 of the output bearing 72.
本実施形態では、出力軸16とキャリヤ30と一体的に回転するように溶接等により固定されている。図示の例では、出力軸フランジ部16bとフランジ部32とが溶接等により固定され、フランジ部32とキャリヤ本体部31が溶接等により固定されている。また、出力軸フランジ部16bがピニオンシャフト23を支持し、キャリヤ30の一部として機能している。言い換えると、出力軸16の一部がキャリヤ30の一部として機能している。
In this embodiment, the output shaft 16 and the carrier 30 are fixed by welding or the like so that they rotate together. In the illustrated example, the output shaft flange portion 16b and the flange portion 32 are fixed by welding or the like, and the flange portion 32 and the carrier body portion 31 are fixed by welding or the like. Further, the output shaft flange portion 16b supports the pinion shaft 23 and functions as a part of the carrier 30. In other words, a portion of the output shaft 16 functions as a portion of the carrier 30.
本実施形態では、突出部58は、油受け部80よりも径方向Rの内側において、側壁面55から軸方向第2側X2に突出するように形成されている。また、突出部58の内径側には雌ねじが形成され、筒状の係止部材78の外周面に形成された雄ねじと螺合する。また、筒状の係止部材78の内周側には、出力軸受72に供給された油を油受け部80に流す油路(図示の例ではスプライン)が形成されている。油受け部80に受け止められた油は、当該油受け部80の形状によってピニオンシャフト23内に形成された空間23aに供給される。
In the present embodiment, the protruding portion 58 is formed to protrude from the side wall surface 55 toward the second axial side X2 on the inner side of the oil receiving portion 80 in the radial direction R. Further, a female thread is formed on the inner diameter side of the protrusion 58, and is screwed into a male thread formed on the outer peripheral surface of the cylindrical locking member 78. Further, an oil passage (a spline in the illustrated example) is formed on the inner circumferential side of the cylindrical locking member 78 to allow oil supplied to the output bearing 72 to flow into the oil receiver 80 . The oil received by the oil receiver 80 is supplied to the space 23a formed within the pinion shaft 23 due to the shape of the oil receiver 80.
本実施形態では、ピニオン22に、ピニオン22の内周面とピニオン22の外周面を径方向Rに連通するピニオン貫通孔38cが形成されている。ピニオン軸受73に供給された油は、ピニオン貫通孔38cによりサンギヤ21とピニオン22との噛み合い部に供給される。
In this embodiment, the pinion 22 is formed with a pinion through hole 38c that communicates the inner circumferential surface of the pinion 22 with the outer circumferential surface of the pinion 22 in the radial direction R. The oil supplied to the pinion bearing 73 is supplied to the meshing portion between the sun gear 21 and the pinion 22 through the pinion through hole 38c.
〔その他の実施形態〕
次に駆動伝達装置10のその他の実施形態について説明する。 [Other embodiments]
Next, other embodiments of thedrive transmission device 10 will be described.
次に駆動伝達装置10のその他の実施形態について説明する。 [Other embodiments]
Next, other embodiments of the
(1)上記第1及び第2の実施形態では、駆動伝達装置10が回転電機等の駆動源12を備えた車両11に搭載された場合を例として説明した。ここで、駆動源12は、回転電機のみ限られず、内燃機関、或いは、内燃機関と回転電機とのハイブリッドでもよい。すなわち、車両11は、内燃機関のみを駆動源12とする自動車、内燃機関及び回転電機を駆動源12とするハイブリッド自動車、電気自動車等であって良い。また、この駆動伝達装置10は、自動車以外の車両11に搭載されても良い。また、駆動伝達装置10は、例えば、図7に示すように、インホイールモータ方式の駆動装置に用いられても好適である。
(1) In the first and second embodiments, the drive transmission device 10 is mounted on a vehicle 11 equipped with a drive source 12 such as a rotating electrical machine. Here, the drive source 12 is not limited to a rotating electrical machine, but may be an internal combustion engine or a hybrid of an internal combustion engine and a rotating electrical machine. That is, the vehicle 11 may be a car that uses only an internal combustion engine as the drive source 12, a hybrid car that uses the internal combustion engine and a rotating electric machine as the drive source 12, an electric car, or the like. Moreover, this drive transmission device 10 may be mounted on a vehicle 11 other than an automobile. The drive transmission device 10 is also suitable for use in an in-wheel motor type drive device, as shown in FIG. 7, for example.
(2)上記第1及び第2の実施形態では、掻き上げ部35が外歯のギヤ状に形成される構成を例として説明した。しかし、そのような構成に限定されることなく、例えば、掻き上げ部35は、軸方向Xの凹凸が周方向Cに並ぶように形成されていても良い、或いは、掻き上げ部35は、径方向Rの凹凸と軸方向Xの凹凸との双方を備え、それらの凹凸が周方向Cに並ぶように形成されていても良い。
(2) In the first and second embodiments, the configuration in which the scraping portion 35 is formed in the shape of a gear with external teeth has been described as an example. However, without being limited to such a configuration, for example, the scraping part 35 may be formed such that unevenness in the axial direction It may be provided with both unevenness in the direction R and unevenness in the axial direction X, and the unevenness may be formed so as to be lined up in the circumferential direction C.
(3)上記第1及び第2の実施形態では、油受け部80が全周に亘って連続的に形成されている構成を例として説明した。しかし、そのような構成に限定されることなく、例えば、油受け部80が軸方向貫通孔38aの付近のみに設けられる構成であっても良い。また、上記第1及び第2の実施形態では、油受け部80がキャリヤ30とは別部材であって、キャリヤ30に固定されている構成を例として説明したが、これには限定されず、油受け部80がキャリヤ30と一体的に形成されていても良い。また、駆動伝達装置10は油受け部80を備えていなくても良い。また、上記第1及び第2の実施形態では、潤滑必要箇所70が、入力軸受71、出力軸受72、及び、ピニオン軸受73を含むものとして説明したが、これらが潤滑必要箇所70に含まれていなくても良い。
(3) In the first and second embodiments, the oil receiving portion 80 is continuously formed over the entire circumference. However, without being limited to such a configuration, for example, a configuration may be adopted in which the oil receiving portion 80 is provided only in the vicinity of the axial through hole 38a. Further, in the first and second embodiments, the oil receiver 80 is a separate member from the carrier 30 and is fixed to the carrier 30. However, the present invention is not limited to this. The oil receiving portion 80 may be formed integrally with the carrier 30. Furthermore, the drive transmission device 10 does not need to include the oil receiver 80. Furthermore, in the first and second embodiments described above, the lubrication-requiring parts 70 are described as including the input bearing 71, the output bearing 72, and the pinion bearing 73, but these are not included in the lubrication-requiring parts 70. You don't have to.
(4)上記第1及び第2の実施形態では、ケース50に、油供給経路Rtとして、対向内周面53、上側凹部54、油受け面54a、側壁面55、油溝57、突出部58、突出外周面58a、突出端面58b、及び、第1連通油路61から第4連通油路64が設けられている構成を例として説明した。しかし、そのような構成に限定されることなく、油供給経路Rtは、これらの一部のみによって構成されていても良い。また例えば、溝や貫通孔を備えず、ケース50の内面のみによって油供給経路Rtが構成されていても良い。
(4) In the first and second embodiments, the case 50 includes the opposing inner peripheral surface 53, the upper recess 54, the oil receiving surface 54a, the side wall surface 55, the oil groove 57, and the protrusion 58 as the oil supply path Rt. , a configuration in which the protruding outer circumferential surface 58a, the protruding end surface 58b, and the first to fourth communicating oil passages 61 to 64 are provided has been described as an example. However, the oil supply route Rt may be configured by only a part of these without being limited to such a configuration. Further, for example, the oil supply path Rt may be configured only by the inner surface of the case 50 without providing a groove or a through hole.
(5)上記第1の実施形態では、車両11の前進中の掻き上げ部35の回転により、第2の実施形態では、車両11の後進中の掻き上げ部35の回転により、油を軸方向第1側X1に向けて飛ばすような向きに掻き上げ部35が形成されている構成を例として説明した。しかし、そのような構成に限定されることなく、例えば、第1の実施形態において車両11の後進中の掻き上げ部35の回転により、第2の実施形態において車両11の前進中の掻き上げ部35の回転により、油を軸方向第1側X1に向けて飛ばすような向きに掻き上げ部35が形成されていてもよい。
(5) In the first embodiment, the rotation of the scraping unit 35 while the vehicle 11 is moving forward, and in the second embodiment, the rotation of the scraping unit 35 while the vehicle 11 is moving backward, moves the oil in the axial direction. The explanation has been given by taking as an example a configuration in which the scraping portion 35 is formed in such a direction as to fly toward the first side X1. However, without being limited to such a configuration, for example, the rotation of the rake-up portion 35 while the vehicle 11 is moving backward in the first embodiment causes the rake-up portion 35 to rotate while the vehicle 11 is moving forward in the second embodiment. The scraping portion 35 may be formed in such a direction that the oil is blown toward the first side X1 in the axial direction by the rotation of the portion 35 .
(6)上記第2の実施形態では、駆動伝達装置10がオイルポンプ110を備え、オイルポンプ110がポンプ駆動ギヤ111により車両11の前進中に駆動される構成を例として説明した。しかし、そのような構成に限定されることなく、例えば、第2の実施形態において駆動伝達装置10がオイルポンプ110を備えていなくてもよい。また、例えば、第1の実施形態において駆動伝達装置10がオイルポンプ110を備えていてもよい。また、例えば、オイルポンプ110が並列の歯車ではなくチェーンやベルト等を介し、入力軸15又は出力軸16の回転に伴って駆動されてもよい。また、例えば、オイルポンプ110が電動式のオイルポンプであってもよい。また、例えば、車両11の後進中に、又は、前進中及び後進中にオイルポンプ110により油供給経路Rtに油が供給されてもよい。また、例えば、車両11の前進中に、又は、後進中にオイルポンプ110と掻き上げ部35との両方により油供給経路Rtに油が供給されてもよい。
(6) In the second embodiment, the drive transmission device 10 includes the oil pump 110, and the oil pump 110 is driven by the pump drive gear 111 while the vehicle 11 is moving forward. However, the present invention is not limited to such a configuration, and, for example, the drive transmission device 10 in the second embodiment may not include the oil pump 110. Further, for example, the drive transmission device 10 may include the oil pump 110 in the first embodiment. Further, for example, the oil pump 110 may be driven with the rotation of the input shaft 15 or the output shaft 16 via a chain, a belt, or the like instead of parallel gears. Further, for example, the oil pump 110 may be an electric oil pump. Further, for example, oil may be supplied to the oil supply path Rt by the oil pump 110 while the vehicle 11 is moving backward, or while the vehicle 11 is moving forward or backward. Further, for example, oil may be supplied to the oil supply path Rt by both the oil pump 110 and the scraping section 35 while the vehicle 11 is moving forward or backward.
(7)なお、上述した実施形態で開示された構成は、矛盾が生じない限り、他の実施形態で開示された構成と組み合わせて適用することも可能である。その他の構成に関しても、本明細書において開示された実施形態は全ての点で単なる例示に過ぎない。従って、本開示の趣旨を逸脱しない範囲内で、適宜、種々の改変を行うことが可能である。
(7) Note that the configuration disclosed in the embodiment described above can also be applied in combination with the configuration disclosed in other embodiments, unless a contradiction occurs. Regarding other configurations, the embodiments disclosed herein are merely illustrative in all respects. Therefore, various modifications can be made as appropriate without departing from the spirit of the present disclosure.
〔本実施形態のまとめ〕
以下、上記において説明した駆動伝達装置の概要について簡単に説明する。 [Summary of this embodiment]
The outline of the drive transmission device described above will be briefly explained below.
以下、上記において説明した駆動伝達装置の概要について簡単に説明する。 [Summary of this embodiment]
The outline of the drive transmission device described above will be briefly explained below.
一態様として、駆動源(12)に駆動連結される入力軸(15)と、車輪(14)に駆動連結される出力軸(16)と、入力軸(15)の回転を減速して出力軸(16)に伝達する減速用の遊星歯車機構(20)と、遊星歯車機構(20)を収容するケース(50)と、を備えた駆動伝達装置(10)であって、遊星歯車機構(20)は、入力軸(15)と一体的に回転するように連結されたサンギヤ(21)と、ピニオン(22)を支持すると共に出力軸(16)と一体的に回転するように連結されたキャリヤ(30)と、ケース(50)に固定されたリングギヤ(25)と、を備え、キャリヤ(30)の外周部に、ケース(50)内の油を掻き上げるための掻き上げ部(35)が設けられ、キャリヤ(30)の回転軸心(Xc)に沿う方向を軸方向(X)とし、鉛直方向に沿う方向を上下方向(Z)として、掻き上げ部(35)は、リングギヤ(25)に対して軸方向Xの一方側に配置され、掻き上げ部(35)の回転軌跡の下端(Tf)が、ピニオン(22)の公転軌跡の下端(Tp)よりも下側(Z2)に配置され、ケース(50)に、掻き上げ部(35)により掻き上げられた油を潤滑必要箇所(70)へ流す油供給経路(Rt)が形成されている。
In one aspect, the input shaft (15) is drivingly connected to the drive source (12), the output shaft (16) is drivingly connected to the wheels (14), and the rotation of the input shaft (15) is decelerated and the output shaft is A drive transmission device (10) comprising a planetary gear mechanism (20) for deceleration that transmits data to the planetary gear mechanism (20), and a case (50) that accommodates the planetary gear mechanism (20). ) includes a sun gear (21) connected to rotate integrally with the input shaft (15), and a carrier supporting the pinion (22) and connected to rotate integrally with the output shaft (16). (30), and a ring gear (25) fixed to the case (50), and a scraping part (35) for scraping up oil in the case (50) is provided on the outer periphery of the carrier (30). The scraping part (35) is provided with a ring gear (25), with the direction along the rotation axis (Xc) of the carrier (30) being the axial direction (X), and the direction along the vertical direction being the vertical direction (Z). The lower end (Tf) of the rotation trajectory of the scraping part (35) is located below (Z2) than the lower end (Tp) of the revolution trajectory of the pinion (22). An oil supply path (Rt) is formed in the case (50) to flow the oil scraped up by the scraping portion (35) to the location requiring lubrication (70).
この構成によれば、油面がピニオンの公転軌跡の下端よりも下側にある場合でも掻き上げ部により油を掻き上げて潤滑必要箇所に油を供給することができるので、ピニオンが油に浸かる割合を少なくしてピニオンによる油の撹拌を少なく抑え易い。従って、油の撹拌による遊星歯車機構の回転抵抗を少なく抑えつつ、掻き上げ部による油の掻き上げを適切に行うことができる。
According to this configuration, even if the oil level is below the lower end of the pinion's orbit, the scraping section can scrape up the oil and supply oil to areas that require lubrication, so the pinion is not submerged in oil. By reducing the ratio, it is easy to suppress oil agitation by the pinion. Therefore, the oil can be appropriately scraped up by the scraping section while minimizing the rotational resistance of the planetary gear mechanism due to stirring of the oil.
一態様として、掻き上げ部(35)は、キャリヤ(30)に設けられたフランジ部(32)の外周面に形成された外歯のギヤ状に形成され、回転軸心(Xc)に直交する方向を径方向(R)とし、回転軸心(Xc)の周りを周回する方向を周方向(C)として、ケース(50)は、掻き上げ部(35)に対して径方向Rの外側から対向する対向内周面(53)を備え、対向内周面(53)は、回転軸心Xcよりも上側(Z1)に配置され、軸方向(X)に沿う軸方向視で掻き上げ部(35)の回転軌跡における外縁(Cf)の接線に交差するように配置された油受け面(54a)を備える、と好適である。
In one aspect, the scraping part (35) is formed in the shape of a gear with external teeth formed on the outer peripheral surface of the flange part (32) provided on the carrier (30), and is perpendicular to the rotation axis (Xc). The direction is defined as the radial direction (R), and the direction of rotation around the rotational axis (Xc) is defined as the circumferential direction (C). The opposing inner circumferential surfaces (53) are disposed above (Z1) than the rotation axis Xc, and the raking portion ( 35) is preferably provided with an oil receiving surface (54a) arranged to intersect with a tangent to the outer edge (Cf) in the rotation locus.
この構成によれば、掻き上げ部により掻き上げた油をキャリヤの回転軸心よりも上側で受け止めて、そこから重力を用いて油供給経路に沿って潤滑必要箇所に油を流すことができる。従って、オイルポンプ等を用いることなく、潤滑必要箇所に適切に油を供給することができる。
According to this configuration, the oil scraped up by the scraping part can be received above the rotational axis of the carrier, and from there, the oil can be flowed along the oil supply path to the locations requiring lubrication using gravity. Therefore, oil can be appropriately supplied to locations that require lubrication without using an oil pump or the like.
一態様として、軸方向(X)における、リングギヤ(25)に対して掻き上げ部(35)が配置されている側を軸方向第1側(X1)とし、その反対側を軸方向第2側(X2)とし、回転軸心(Xc)に直交する方向を径方向(R)として、掻き上げ部(35)よりも径方向(R)の内側に配置されて径方向(R)の内側に向けて開口するように形成された油受け部(80)を更に備え、ケース(50)は、キャリヤ(30)に対して軸方向第1側(X1)に配置され、軸方向第2側(X2)を向く側壁面(55)を備え、掻き上げ部(35)は、リングギヤ(25)と側壁面(55)との軸方向Xの間に配置され、油受け部(80)は、キャリヤ(30)と側壁面(55)との軸方向Xの間に配置され、キャリヤ(30)に固定され、ケース(50)は、油受け部(80)よりも径方向(R)の内側において、側壁面(55)よりも軸方向第2側(X2)に突出するように形成され、径方向(R)に沿う径方向視で油受け部(80)と重複するように配置された突出部(58)を更に備え、潤滑必要箇所(70)には、ピニオン(22)をキャリヤ(30)に対して回転自在に支持するピニオン軸受(73)が含まれ、キャリヤ(30)には、油受け部(80)とピニオン軸受(73)とを連通するキャリヤ内油路(38)が形成されている、と好適である。
As one aspect, in the axial direction (X), the side where the scraping part (35) is arranged with respect to the ring gear (25) is defined as the first axial side (X1), and the opposite side thereof is defined as the second axial side. (X2), and the direction perpendicular to the rotational axis (Xc) is defined as the radial direction (R). The case (50) is arranged on the first axial side (X1) with respect to the carrier (30) and on the second axial side (X1) with respect to the carrier (30). The scraping part (35) is arranged between the ring gear (25) and the side wall surface (55) in the axial direction X, and the oil receiving part (80) (30) and the side wall surface (55) in the axial direction X, and is fixed to the carrier (30). , a protrusion formed to protrude from the side wall surface (55) toward the second axial side (X2) and arranged to overlap with the oil receiver (80) when viewed in the radial direction (R). The lubrication required portion (70) includes a pinion bearing (73) that rotatably supports the pinion (22) relative to the carrier (30), and the carrier (30) includes a portion (58) that requires lubrication. Preferably, an in-carrier oil passage (38) is formed that communicates the oil receiver (80) and the pinion bearing (73).
この構成によれば、掻き上げ部により掻き上げられた油が、側壁面から突出部に流れ、突出部の外面に沿って流れてから落下した油が油受け部により受け止められる。そして、油受け部からピニオン軸受に油が供給される。従って、掻き上げ部により掻き上げられた油により、ピニオンを支持するピニオン軸受を適切に潤滑することができる。
According to this configuration, the oil scraped up by the scraping part flows from the side wall surface to the protruding part, and the oil that flows along the outer surface of the protruding part and then falls is received by the oil receiving part. Oil is then supplied to the pinion bearing from the oil receiver. Therefore, the oil scraped up by the scraping part can appropriately lubricate the pinion bearing that supports the pinion.
一態様として、軸方向(X)における、リングギヤ(25)に対して掻き上げ部(35)が配置されている側を軸方向第1側(X1)とし、その反対側を軸方向第2側(X2)とし、ケース(50)は、キャリヤ(30)に対して軸方向第1側(X1)に配置され、軸方向第2側(X2)を向く側壁面(55)を備え、側壁面(55)に、潤滑必要箇所(70)に連通する油溝(57)が形成され、油溝(57)は、軸方向第2側(X2)に向けて開口し、掻き上げ部(35)は、キャリヤ(30)に設けられたフランジ部(32)の外周面に形成された外歯のはすばギヤ状に形成され、車両(11)の前進中の掻き上げ部(35)の回転によって、油を軸方向第1側(X1)に向けて飛ばすような向きに形成されている、と好適である。
As one aspect, in the axial direction (X), the side where the scraping part (35) is arranged with respect to the ring gear (25) is defined as the first axial side (X1), and the opposite side thereof is defined as the second axial side. (X2), the case (50) is disposed on the first axial side (X1) with respect to the carrier (30), and includes a side wall surface (55) facing the second axial side (X2). (55) is formed with an oil groove (57) that communicates with the lubrication required location (70), the oil groove (57) opens toward the second axial side (X2), and the raking portion (35) is formed in the shape of a helical gear with external teeth formed on the outer peripheral surface of the flange portion (32) provided on the carrier (30), and is configured to rotate the scraping portion (35) while the vehicle (11) is moving forward. Accordingly, it is preferable that the oil is oriented such that the oil is blown toward the first side (X1) in the axial direction.
この構成によれば、掻き上げた油を油溝に多く供給できる。よって、油溝から潤滑必要箇所に油を適切に供給できる。
According to this configuration, a large amount of the scraped up oil can be supplied to the oil groove. Therefore, oil can be appropriately supplied from the oil groove to locations that require lubrication.
一態様として、入力軸(71)と出力軸(72)とが同軸上に配置されていると共に、入力軸(71)と出力軸(72)とが軸方向(X)に並んで配置され、潤滑必要箇所(70)には、入力軸(71)をケース(50)に対して回転自在に支持する入力軸受(71)と、出力軸(72)をケース(50)に対して回転自在に支持する出力軸受(72)と、が含まれ、回転軸心(Xc)に直交する方向を径方向(R)として、ケース(50)は、入力軸受(71)を径方向(R)の外側から支持する筒状の第1筒状部(51)と、出力軸受(72)を径方向Rの外側から支持する筒状の第2筒状部(52)と、を備えている。第1筒状部(51)には、第1筒状部(51)の外周面における上側(Z1)を向く部分と入力軸受(71)を支持する内周面とを連通する第1連通油路(61)が形成されている。また、第2筒状部(52)には、第2筒状部(52)の外周面における上側(Z1)を向く部分と出力軸受(72)を支持する内周面とを連通する第2連通油路(62)が形成されている、と好適である。
In one embodiment, the input shaft (71) and the output shaft (72) are arranged coaxially, and the input shaft (71) and the output shaft (72) are arranged side by side in the axial direction (X), The parts (70) that require lubrication include an input bearing (71) that rotatably supports the input shaft (71) with respect to the case (50), and an input bearing (71) that rotatably supports the output shaft (72) with respect to the case (50). The case (50) includes an output bearing (72) to support, and the direction perpendicular to the rotation axis (Xc) is defined as the radial direction (R), and the case (50) supports the input bearing (71) on the outside in the radial direction (R). A cylindrical first cylindrical part (51) that supports the output bearing (72) from the outside in the radial direction R is provided. The first cylindrical portion (51) has a first communicating oil that communicates between the portion of the outer peripheral surface of the first cylindrical portion (51) facing upward (Z1) and the inner peripheral surface that supports the input bearing (71). A channel (61) is formed. The second cylindrical portion (52) also has a second cylindrical portion that communicates between the portion of the outer circumferential surface of the second cylindrical portion (52) facing upward (Z1) and the inner circumferential surface that supports the output bearing (72). Preferably, a communicating oil passage (62) is formed.
この構成によれば、掻き上げ部により掻き上げられ第1筒状部の外周面における上側を向く部分に到達した油の一部が、第1連通油路に入る。そして、当該第1連通油路に入った油は入力軸受に到達することになる。これにより、入力軸受を潤滑することができる。また、掻き上げ部により掻き上げられ、上記のように側壁面或いは油溝に沿って第2筒状部の外周面における上側を向く部分に到達した油の一部が、第2連通油路に入る。そして、当該第2連通油路に入った油は出力軸受に到達することになる。これにより、出力軸受を潤滑することができる。これにより、例えば、入力軸及び出力軸の内部に油路を設けることなく、各軸受を潤滑することができる。
According to this configuration, a portion of the oil that has been scraped up by the scraping portion and has reached the upwardly facing portion of the outer circumferential surface of the first cylindrical portion enters the first communication oil passage. The oil that has entered the first communication oil passage then reaches the input bearing. This allows the input bearing to be lubricated. In addition, some of the oil that has been scooped up by the scraping section and has reached the upwardly facing portion of the outer circumferential surface of the second cylindrical section along the side wall surface or oil groove as described above flows into the second communicating oil passage. enter. The oil that has entered the second communication oil passage then reaches the output bearing. This allows the output bearing to be lubricated. Thereby, each bearing can be lubricated, for example, without providing oil passages inside the input shaft and the output shaft.
10:駆動伝達装置、15:入力軸、16:出力軸、11:車両、12:駆動源、14:車輪、20:遊星歯車機構、21:サンギヤ、22:ピニオン、25:リングギヤ、30:キャリヤ、32:フランジ部、35:掻き上げ部、38:キャリヤ内油路、50:ケース、51:第1筒状部、52:第2筒状部、53:対向内周面、54a:油受け面、55:側壁面、57:油溝、58:突出部、61:第1連通油路、62:第2連通油路、70:潤滑必要箇所、71:入力軸受、72:出力軸受、73:ピニオン軸受、80:油受け部、Xc:キャリヤの回転軸心、Rt:油供給経路、Tf:掻き上げ部の回転軌跡の下端、Tp:ピニオンの公転軌跡の下端
10: Drive transmission device, 15: Input shaft, 16: Output shaft, 11: Vehicle, 12: Drive source, 14: Wheel, 20: Planetary gear mechanism, 21: Sun gear, 22: Pinion, 25: Ring gear, 30: Carrier , 32: flange part, 35: scraping part, 38: oil path in carrier, 50: case, 51: first cylindrical part, 52: second cylindrical part, 53: opposing inner peripheral surface, 54a: oil receiver surface, 55: side wall surface, 57: oil groove, 58: protrusion, 61: first communicating oil passage, 62: second communicating oil passage, 70: location requiring lubrication, 71: input bearing, 72: output bearing, 73 : pinion bearing, 80: oil receiving part, Xc: rotation axis of carrier, Rt: oil supply path, Tf: lower end of rotation trajectory of scraping part, Tp: lower end of pinion revolution trajectory
Claims (5)
- 駆動源に駆動連結される入力軸と、
車輪に駆動連結される出力軸と、
前記入力軸の回転を減速して前記出力軸に伝達する減速用の遊星歯車機構と、
前記遊星歯車機構を収容するケースと、
を備えた車両用駆動伝達装置であって、
前記遊星歯車機構は、前記入力軸と一体的に回転するように連結されたサンギヤと、ピニオンを支持すると共に前記出力軸と一体的に回転するように連結されたキャリヤと、前記ケースに固定されたリングギヤと、を備え、
前記キャリヤの外周部に、前記ケース内の油を掻き上げるための掻き上げ部が設けられ、
前記キャリヤの回転軸心に沿う方向を軸方向とし、鉛直方向に沿う方向を上下方向として、
前記掻き上げ部は、前記リングギヤに対して軸方向の一方側に配置され、
前記掻き上げ部の回転軌跡の下端が、前記ピニオンの公転軌跡の下端よりも下側に配置され、
前記ケースに、前記掻き上げ部により掻き上げられた油を潤滑必要箇所へ流す油供給経路が形成されている、車両用駆動伝達装置。 an input shaft drivingly connected to a driving source;
an output shaft drive-coupled to the wheels;
a planetary gear mechanism for decelerating the rotation of the input shaft and transmitting the rotation to the output shaft;
a case housing the planetary gear mechanism;
A vehicle drive transmission device comprising:
The planetary gear mechanism includes a sun gear connected to rotate integrally with the input shaft, a carrier supporting a pinion and connected to rotate integrally with the output shaft, and a carrier fixed to the case. a ring gear;
A scraping part for scraping up oil in the case is provided on the outer periphery of the carrier,
The direction along the rotational axis of the carrier is defined as the axial direction, and the direction along the vertical direction is defined as the vertical direction,
The scraping part is arranged on one side in the axial direction with respect to the ring gear,
The lower end of the rotation trajectory of the scraping part is arranged below the lower end of the revolution trajectory of the pinion,
A drive transmission device for a vehicle, wherein the case is formed with an oil supply path through which oil scraped up by the scraping portion flows to a location requiring lubrication. - 前記掻き上げ部は、前記キャリヤに設けられたフランジ部の外周面に形成された外歯のギヤ状に形成され、
前記回転軸心に直交する方向を径方向とし、前記回転軸心の周りを周回する方向を周方向として、
前記ケースは、前記掻き上げ部に対して前記径方向の外側から対向する対向内周面を備え、
前記対向内周面は、前記回転軸心よりも上側に配置され、前記軸方向に沿う軸方向視で前記掻き上げ部の回転軌跡における外縁の接線に交差するように配置された油受け面を備える、請求項1に記載の車両用駆動伝達装置。 The scraping part is formed in the shape of a gear of external teeth formed on the outer peripheral surface of a flange part provided on the carrier,
A direction perpendicular to the rotational axis is defined as a radial direction, and a direction around the rotational axis is defined as a circumferential direction,
The case includes an inner circumferential surface facing the scraping portion from the outside in the radial direction,
The opposing inner circumferential surface has an oil receiving surface that is arranged above the rotation axis and intersects with a tangent to the outer edge of the rotation locus of the scraping part when viewed in the axial direction along the axial direction. The vehicular drive transmission device according to claim 1. - 前記軸方向における、前記リングギヤに対して前記掻き上げ部が配置されている側を軸方向第1側とし、その反対側を軸方向第2側とし、前記回転軸心に直交する方向を径方向として、
前記掻き上げ部よりも前記径方向の内側に配置されて前記径方向の内側に向けて開口するように形成された油受け部を更に備え、
前記ケースは、前記キャリヤに対して前記軸方向第1側に配置され、前記軸方向第2側を向く側壁面を備え、
前記掻き上げ部は、前記リングギヤと前記側壁面との前記軸方向の間に配置され、
前記油受け部は、前記キャリヤと前記側壁面との前記軸方向の間に配置され、前記キャリヤに固定され、
前記ケースは、前記油受け部よりも前記径方向の内側において、前記側壁面よりも前記軸方向第2側に突出するように形成され、前記径方向に沿う径方向視で前記油受け部と重複するように配置された突出部を更に備え、
前記潤滑必要箇所には、前記ピニオンを前記キャリヤに対して回転自在に支持するピニオン軸受が含まれ、
前記キャリヤには、前記油受け部と前記ピニオン軸受とを連通するキャリヤ内油路が形成されている、請求項1又は2に記載の車両用駆動伝達装置。 In the axial direction, the side where the scraping part is arranged with respect to the ring gear is the first axial side, the opposite side is the second axial side, and the direction perpendicular to the rotational axis is the radial direction. As,
further comprising an oil receiver disposed inside the radial direction of the scraping part and formed to open toward the radial inside,
The case is disposed on the first axial side with respect to the carrier and includes a side wall surface facing the second axial side,
The scraping part is arranged between the ring gear and the side wall surface in the axial direction,
The oil receiver is disposed between the carrier and the side wall surface in the axial direction, and is fixed to the carrier,
The case is formed so as to protrude toward the second axial side from the side wall surface on the inner side of the oil receiver in the radial direction, and is configured to be in contact with the oil receiver when viewed in the radial direction along the radial direction. further comprising protrusions arranged in an overlapping manner;
The locations requiring lubrication include a pinion bearing that rotatably supports the pinion with respect to the carrier;
3. The vehicle drive transmission device according to claim 1, wherein the carrier has an in-carrier oil passage that communicates the oil receiver and the pinion bearing. - 前記軸方向における、前記リングギヤに対して前記掻き上げ部が配置されている側を軸方向第1側とし、その反対側を軸方向第2側とし、
前記ケースは、前記キャリヤに対して前記軸方向第1側に配置され、前記軸方向第2側を向く側壁面を備え、
前記側壁面に、前記潤滑必要箇所に連通する油溝が形成され、
前記油溝は、前記軸方向第2側に向けて開口し、
前記掻き上げ部は、前記キャリヤに設けられたフランジ部の外周面に形成された外歯のはすばギヤ状に形成され、車両の前進中の前記掻き上げ部の回転によって、油を前記軸方向第1側に向けて飛ばすような向きに形成されている、請求項1から3のいずれか一項に記載の車両用駆動伝達装置。 In the axial direction, the side on which the scraping part is arranged with respect to the ring gear is defined as a first axial side, and the opposite side is defined as a second axial side,
The case is disposed on the first axial side with respect to the carrier and includes a side wall surface facing the second axial side,
An oil groove communicating with the location requiring lubrication is formed on the side wall surface,
The oil groove opens toward the second axial side,
The scraping portion is formed in the shape of a helical gear with external teeth formed on the outer circumferential surface of a flange portion provided on the carrier, and the rotation of the scraping portion while the vehicle is moving moves the oil to the shaft. The vehicle drive transmission device according to any one of claims 1 to 3, wherein the vehicle drive transmission device is oriented so as to fly toward the first direction side. - 前記入力軸と前記出力軸とが同軸上に配置されていると共に、前記入力軸と前記出力軸とが前記軸方向に並んで配置され、
前記潤滑必要箇所には、前記入力軸を前記ケースに対して回転自在に支持する入力軸受と、前記出力軸を前記ケースに対して回転自在に支持する出力軸受と、が含まれ、
前記回転軸心に直交する方向を径方向として、
前記ケースは、前記入力軸受を前記径方向の外側から支持する筒状の第1筒状部と、前記出力軸受を前記径方向の外側から支持する筒状の第2筒状部と、を備え、
前記第1筒状部には、当該第1筒状部の外周面における上側を向く部分と前記入力軸受を支持する内周面とを連通する第1連通油路が形成され、
前記第2筒状部には、当該第2筒状部の外周面における上側を向く部分と前記出力軸受を支持する内周面とを連通する第2連通油路が形成されている、請求項1から4のいずれか一項に記載の車両用駆動伝達装置。 The input shaft and the output shaft are arranged coaxially, and the input shaft and the output shaft are arranged side by side in the axial direction,
The locations requiring lubrication include an input bearing that rotatably supports the input shaft with respect to the case, and an output bearing that rotatably supports the output shaft with respect to the case,
The direction perpendicular to the rotational axis is defined as the radial direction,
The case includes a first cylindrical part that supports the input bearing from the outside in the radial direction, and a second cylindrical part that supports the output bearing from the outside in the radial direction. ,
A first communication oil passage is formed in the first cylindrical portion, which communicates an upwardly facing portion of the outer circumferential surface of the first cylindrical portion with an inner circumferential surface that supports the input bearing;
A second communicating oil passage is formed in the second cylindrical portion, which communicates an upwardly facing portion of the outer circumferential surface of the second cylindrical portion with an inner circumferential surface that supports the output bearing. 5. The vehicle drive transmission device according to any one of 1 to 4.
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