JP2015183762A - Lubrication structure of drive power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a drive power transmission device lubrication structure capable of appropriately lubricating gears of a transmission and a differential gear.SOLUTION: A power transmission device comprises a differential gear DF. The differential gear DF includes an outer member 302, an orthogonal shaft 304, bevel gears 306, 308, and side gears 310, 312. A drive shaft 316 on the other side passing through an output shaft 3 is connected to the other side gear 312. A planetary gear mechanism 200 is provided in the output shaft 3. Lubricating oil is stored in the outer member 302. The lubricating oil in the outer member 302 is supplied to the planetary gear mechanism 200 via a supply line 329 provided in the drive shaft 316 on the other side. The lubricating oil scattered by the rotation of the planetary gear mechanism 200 is returned into the outer member 302 via a gutter portion 322 provided in an upper portion of a casing 301 and a return oil line 326.

Description

  The present invention relates to a lubrication structure for a driving force transmission device.

  Conventionally, a differential gear lubrication structure is known as a driving force transmission device (see, for example, Patent Document 1).

JP 2013-194771 A

  In the case of a driving force transmission device in which the gear of the transmission is arranged concentrically with the rotational center shaft of the differential gear, if the amount of lubrication is adjusted so as not to cause stirring resistance with respect to the gear of the transmission, the amount of lubrication to the differential gear is reduced. There is a risk of running out.

  On the other hand, if you try to supply the lubricating oil so that it can be properly lubricated on the basis of the differential gear, the lubricating oil to the transmission gear becomes excessive, and the lubricating oil becomes a stirring resistance when the transmission gear rotates. There is a risk that the efficiency of the transmission will decrease.

  In view of the above, an object of the present invention is to provide a lubrication structure for a driving force transmission device that can appropriately lubricate a gear and a differential gear of a transmission.

[1] In order to achieve the above object, the present invention provides:
A lubrication structure for a power transmission device comprising a differential gear arranged concentrically with an output shaft of a transmission,
The differential gear includes an outer member connected to one end of the output shaft, an orthogonal shaft provided in the outer member and extending orthogonally to the axial direction of the output shaft, A pair of bevel gears facing each other between the axial directions of the shafts and rotatably provided on the orthogonal shaft, and a pair of side gears facing each other and meshing with the pair of bevel gears,
One side gear is provided with a one-side drive shaft extending in one of the axial directions of the output shaft,
The other side gear is provided with the other side drive shaft that extends in the other axial direction of the output shaft and passes through the output shaft,
The output shaft is provided with a speed changing rotator,
Lubricating oil is stored in the outer member,
The lubricating oil in the outer member is supplied to the speed change rotating body via a supply path provided in the other drive shaft,
The lubricating oil scattered by the rotation of the speed change rotating body is returned into the outer member through a flange provided at the upper part of the housing and a return oil passage for guiding the lubricating oil received by the flange downward. It is characterized by that.

  According to the present invention, the lubricating oil is stored in the outer member. The lubricating oil supplied to the speed changing rotator is supplied via a supply path provided on the other drive shaft. A part of the lubricating oil scattered by the rotation of the speed changing rotator is returned to the outer member via the flange and the return oil passage. Then, the lubricating oil in the outer member is prevented from being supplied to the transmission rotating body until it reaches the supply path provided in the other drive shaft.

  Accordingly, the supply of excessive lubricating oil to the transmission rotating body is prevented to reduce the agitation resistance, and a sufficient amount of lubricating oil can be supplied to the differential gear, so that the transmission rotating body and the differential gear can be connected to each other. Can be properly lubricated.

  [2] Further, in the present invention, when the outer member and the orthogonal shaft are configured separately, a seal member for preventing leakage of lubricating oil is provided at the connecting portion between the outer member and the orthogonal shaft. It is preferable to provide it.

  According to such a configuration, the lubricating oil can be prevented from leaking from the gap between the outer member and the orthogonal shaft, and the amount of the lubricating oil supplied to the transmission rotating body and the differential gear is appropriately maintained. be able to.

  [3] Further, in the present invention, the speed changing rotator can be constituted by a planetary gear mechanism having a sun gear or a ring gear and a carrier that rotatably and revolves a pinion that meshes with the sun gear or the ring gear.

  [4] Further, in the present invention, when the outer member is pivotally supported by the casing via the pair of bearings, the lubricating oil received by the flange portion is supplied to the one bearing and the casing via the supply path. The outer member or the one-side drive shaft is provided with a spiral groove positioned between the outer member and the one-side drive shaft. This lubricating oil can be configured to be guided into the outer member by the rotation of the one-side drive shaft.

Explanatory drawing which shows embodiment of the power transmission device of this invention in a partial cross section. Explanatory drawing which shows the lever crank mechanism of this embodiment. Explanatory drawing which shows the change of the rotation radius of this embodiment. 3A shows a state where the turning radius is maximum, FIG. 3B shows a case where the turning radius is medium, FIG. 3C shows a case where the turning radius is small, and FIG. 3D shows a state where the turning radius is zero. Explanatory drawing which shows the change of the rocking | fluctuation range of the rocking | fluctuation link with respect to the change of the rotation radius of this embodiment. FIG. 4A shows the swing range when the turning radius is the maximum, FIG. 4B shows the inside of the turning radius, and FIG. 4C shows the swing range when the turning radius is small. The skeleton figure which shows the power transmission device of this embodiment typically. Sectional drawing which shows the differential gear of this embodiment. Explanatory drawing which shows the flow of the lubricating oil of this embodiment. Explanatory drawing which shows the flow of the lubricating oil of this embodiment. Explanatory drawing which shows the flow of the lubricating oil of this embodiment.

  With reference to the drawings, an embodiment of the lubricating structure of the power transmission device of the present invention will be described. The power transmission device of this embodiment includes a four-bar linkage mechanism type continuously variable transmission. The continuously variable transmission is a so-called IVT (Infinity) transmission that can change the speed ratio h (h = rotational speed of the input unit / rotational speed of the output shaft) to infinity (∞) and set the rotational speed of the output shaft to “0”. Variable transmission).

  Referring to FIGS. 1 to 4, a continuously variable transmission 1 of a four-bar linkage mechanism type receives a rotational driving force from a traveling drive source ENG such as an engine or an electric motor that is an internal combustion engine, whereby a rotation center axis P1 is obtained. , An output end 3 that is arranged in parallel to the rotation center axis P1, and that transmits rotational power to the drive wheels (not shown) of the vehicle via the differential gear DF, and the rotation center axis P1. And six turning radius adjusting mechanisms 4 provided on the top.

  Each turning radius adjusting mechanism 4 includes a cam disk 5 as a cam part and a rotating disk 6 as a rotating part. The cam disks 5 have a disk shape, are eccentric from the rotation center axis P <b> 1, and are provided in each rotation radius adjustment mechanism 4 so as to form one set with respect to one rotation radius adjustment mechanism 4. . The cam disk 5 is provided with a through hole 5a penetrating in the direction of the rotation center axis P1. Further, the cam disk 5 is opened in a direction opposite to the direction decentered with respect to the rotation center axis P1, and a notch hole 5b for communicating the outer peripheral surface of the cam disk 5 with the inner peripheral surface constituting the through hole 5a. Is provided.

  Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the rotation center axis P <b> 1 with six sets of cam disks 5 with a phase difference of 60 degrees.

  The cam disk 5 is formed integrally with the cam disk 5 of the adjacent turning radius adjusting mechanism 4 to constitute an integrated cam portion 5c. The integrated cam portion 5c may be formed by integral molding, or may be integrated by welding two cam portions. A pair of cam disks 5 of each turning radius adjusting mechanism 4 are fixed by bolts (not shown). The cam disk 5 located closest to the driving source for traveling on the rotation center axis P1 is formed integrally with the input end 2a. In this way, the input end 2a and the cam disk 5 constitute the input portion 2 (camshaft) as the input shaft.

  The input portion 2 (camshaft) as an input shaft includes an insertion hole 60 configured by connecting through holes 5a of the cam disk 5. Thereby, the input part 2 is comprised in the hollow-shaft shape where the one end on the opposite side to the drive source ENG for driving | running | working opened and the other end was obstruct | occluded. The cam disk 5 located at the other end on the traveling drive source side is formed integrally with the input end 2a. As a method of integrally forming the cam disk 5 and the input end 2a, integral molding may be used, or the cam disk 5 and the input part 2 may be integrated by welding.

  Each set of cam disks 5 is rotatably fitted with a disk-shaped rotating disk 6 having a receiving hole 6a for receiving the cam disk 5 in an eccentric state.

  As shown in FIG. 5, the rotating disk 6 has a cam disk 5 center point P2 and a rotating disk 6 center point P3, a distance Ra between the rotation center axis P1 and the center point P2, and the center point P2 and the center point. It is eccentric with respect to the cam disk 5 so that the distance Rb of P3 is the same.

  The receiving hole 6 a of the rotating disk 6 is provided with internal teeth 6 b that are positioned between the pair of cam disks 5.

  In the insertion hole 60 of the input unit 2, the pinion 70 is positioned concentrically with the rotation center axis P 1 and at a position corresponding to the inner tooth 6 b of the rotary disk 6 so that the pinion 70 can rotate relative to the camshaft 51. Has been placed. The pinion 70 is formed integrally with the pinion shaft 72. The pinion 70 may be configured separately from the pinion shaft 72, and the pinion 70 may be connected to the pinion shaft 72 by spline coupling. In the present embodiment, the term “pinion 70” is defined as including the pinion shaft 72.

  The pinion 70 meshes with the internal teeth 6 b of the rotating disk 6 through the notch hole 5 b of the cam disk 5. The pinion shaft 72 is provided with a bearing 74 positioned between the adjacent pinions 70. The pinion shaft 72 supports the input unit 2 via the bearing 74. The differential mechanism 8 is connected to the pinion shaft 72. The driving force of the adjusting drive source 14 is transmitted to the pinion 70 via the differential mechanism 8.

  The differential mechanism 8 is constituted by a planetary gear mechanism, and meshes with the sun gear, the first ring gear connected to the input unit 2, the second ring gear connected to the pinion shaft 72, the sun gear, and the first ring gear. A carrier that pivotally supports a stepped pinion composed of a large-diameter portion and a small-diameter portion that meshes with the second ring gear so as to rotate and revolve.

  The sun gear is connected to the rotating shaft of the adjusting drive source 14 composed of an electric motor for the pinion shaft 72. If the rotational speed of the adjusting drive source 14 is the same as the rotational speed of the input unit 2, the sun gear and the first ring gear rotate at the same speed, and there are four elements: the sun gear, the first ring gear, the second ring gear, and the carrier. Becomes a locked state where relative rotation is impossible, and the pinion shaft 72 connected to the second ring gear rotates at the same speed as the input unit 2.

  When the rotational speed of the adjustment drive source 14 is made slower than the rotational speed of the input unit 2, the rotational speed of the sun gear is Ns, the rotational speed of the first ring gear is NR1, and the gear ratio between the sun gear and the first ring gear (the teeth of the first ring gear) Number / number of teeth of the sun gear) is j, and the rotational speed of the carrier is (j · NR1 + Ns) / (j + 1). If the gear ratio between the sun gear and the second ring gear ((number of teeth of the second ring gear / number of teeth of the sun gear) × (number of teeth of the large diameter portion of the stepped pinion / number of teeth of the small diameter portion)) is k, The rotational speed of the 2-ring gear is {j (k + 1) NR1 + (k−j) Ns} / {k (j + 1)}.

  Since the rotating disk 6 is eccentric with respect to the cam disk 5 such that the distance Ra and the distance Rb are the same, the center point P3 of the rotating disk 6 is positioned on the same axis as the rotation center axis P1. Thus, the distance between the rotation center axis P1 and the center point P3, that is, the eccentricity R1 can be set to “0”.

  A connecting rod 15 having a large-diameter large-diameter annular portion 15a at one end and a small-diameter annular portion 15b having a smaller diameter than the large-diameter annular portion 15a at the other end is provided at the periphery of the rotating disk 6. A large-diameter annular portion 15a is rotatably fitted via a connecting rod bearing 16 made of a roller bearing. In addition, the connecting rod bearing 16 may comprise two ball bearings arranged in the axial direction as a set. The output shaft 3 is provided with six swing links 18 corresponding to the connecting rod 15 via the first one-way clutch 17.

  The first one-way clutch 17 is provided between the swing link 18 and the output shaft 3, and when the swing link 18 is about to rotate relative to the output shaft 3 on one side, the swing link 18 is connected to the output shaft. The swing link 18 is idled with respect to the output shaft 3 when it is fixed to 3 and tries to rotate relative to the other side.

  The swing link 18 is formed in an annular shape, and a swing end portion 18 a connected to the small diameter annular portion 15 b of the connecting rod 15 is provided above the swing link 18. The swing end portion 18a is provided with a pair of projecting pieces 18b projecting so as to sandwich the small-diameter annular portion 15b in the axial direction. The pair of projecting pieces 18b are provided with insertion holes 18c corresponding to the inner diameter of the small-diameter annular portion 15b. A connecting pin 19 is inserted into the insertion hole 18c and the small diameter annular portion 15b. Thereby, the connecting rod 15 and the swing link 18 are connected.

  In the present embodiment, the oscillating end 18a is disposed below the output shaft 3 so that the oscillating end 18a of the oscillating link 18 is immersed in the oil reservoir of lubricating oil collected below the case 80. Has been. As a result, the oscillating end 18a can be lubricated with the oil reservoir, and the lubricating oil in the oil reservoir can be lifted by the oscillating motion of the oscillating link 18 to lubricate other components of the continuously variable transmission 1. it can.

  In the description of the embodiment, the transmission ratio is defined as the rotational speed of the input unit / the rotational speed of the output shaft.

  FIG. 3 shows the positional relationship between the pinion shaft 72 and the rotating disk 6 in a state where the eccentric amount R1 of the turning radius adjusting mechanism 4 is changed. FIG. 3A shows a state in which the amount of eccentricity R1 is “maximum” so that the rotation center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotation disk 6 are aligned. The pinion shaft 72 and the rotary disk 6 are located. At this time, the gear ratio h is minimized.

  FIG. 3B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 3A, and FIG. 3C illustrates that the eccentric amount R1 is smaller than that in FIG. Is shown. The gear ratio h is “medium” which is larger than the gear ratio h in FIG. 3A in FIG. 3B, and “large” which is larger than the gear ratio h in FIG. 3B in FIG. Become. FIG. 3D shows a state where the eccentricity R1 is “0”, and the rotation center axis P1 and the center point P3 of the rotating disk 6 are located concentrically. The gear ratio h at this time is infinite (∞). In the continuously variable transmission 1 of the first embodiment, the radius of rotational motion on the input unit 2 side can be adjusted by changing the amount of eccentricity R1 by the rotational radius adjusting mechanism 4.

  In the present embodiment, the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 constitute a lever crank mechanism 20 (four-bar linkage mechanism). Then, the lever crank mechanism 20 converts the rotational motion of the input unit 2 into the swing motion of the swing link 18. The continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20. When the input portion 2 is rotated and the pinion shaft 72 is rotated at the same speed as the input portion 2 when the eccentric amount R1 is not “0”, each connecting rod 15 changes its phase by 60 degrees, and the eccentric amount R1. Based on the above, the input unit 2 and the output shaft 3 are swung alternately repeatedly by pushing to the output shaft 3 side or pulling to the input unit 2 side.

  Since the small-diameter annular portion 15b of the connecting rod 15 is connected to the swing link 18 provided on the output shaft 3 via the first one-way clutch 17, the swing link 18 is pushed and pulled by the connecting rod 15 to swing. When the swing link 18 moves, the output shaft 3 rotates only when the swing link 18 rotates in either the pushing direction side or the pulling direction side, and when the swing link 18 rotates in the other direction, the output shaft 3, the force of the swing motion of the swing link 18 is not transmitted, and the swing link 18 rotates idle. Since each turning radius adjusting mechanism 4 is arranged with a phase changed every 60 degrees, the output shaft 3 is rotated in turn by each turning radius adjusting mechanism 4.

  As schematically shown in FIG. 5, the continuously variable transmission 1 of the present embodiment includes a control unit ECU that controls the adjustment drive source 14. The control unit ECU is an electronic unit composed of a CPU, a memory, and the like, and controls the adjustment drive source 14 by executing a control program held in the memory by the CPU, so that the eccentricity of the turning radius adjustment mechanism 4 is controlled. Serves to regulate the amount R1. The control unit ECU also includes information on the accelerator opening from the accelerator opening detecting unit 110 provided in the vehicle, information on the vehicle speed from the vehicle speed detecting unit 111 that detects the traveling speed of the vehicle, and information on the driving source ENG for traveling. It is configured to be able to receive rotational speed information. In the control unit ECU of the present embodiment, the traveling drive source ENG is controlled by estimating the rotational speed of the traveling drive source ENG to be the same as the rotational speed of the input unit 2.

  Further, the continuously variable transmission 1 of the present embodiment uses the rotational load of the driving source ENG for traveling to apply the engine brake to reduce the rotational speed of the output shaft 3 or to reduce the rotational force of the drive wheels. An output speed reduction mechanism 100 is provided for turning the driving source for use. In the case where the traveling drive source is configured by an electric motor, an output speed reduction mechanism can be used so as to perform regeneration using the electric motor as a generator.

  The output speed reduction mechanism 100 is disposed between the output shaft 3 and the differential gear DF. The output speed reduction mechanism 100 includes an input side sprocket 101 fixed to the input unit 2, an output side sprocket 102 rotatably supported on the output shaft 3, a chain 103 wound around both the sprockets 101, 102, The second one-way clutch 104 provided on the output shaft 3 and the output-side sprocket 102 can be switched between a connected state in which the output-side sprocket 102 is connected to the output shaft 3 via the second one-way clutch 104 and an open state in which this connection is disconnected. And a dog clutch 105 as a coupling mechanism (meshing mechanism).

  The second one-way clutch 104 is provided between the dog clutch 105 and the output shaft 3, and when the dog clutch 105 attempts to rotate relative to the output shaft 3 on one side, the dog clutch 105 idles and rotates on the other side. The dog clutch 105 is configured to be fixed to the output shaft 3 when trying to do so.

  In the continuously variable transmission 1 of the present embodiment, when the output deceleration mechanism 100 is operated to apply the engine brake, or the traveling drive source ENG is rotated using the rotational force of the driving wheel, the fuel cut is performed. When it is desired to improve the fuel consumption, the dog clutch 105 is brought into a connected state. As a result, if the second one-way clutch 104 functions and the output-side sprocket 102 is fixed to the output shaft 3, the output deceleration mechanism 100 can apply engine braking or improve fuel efficiency.

  As shown in FIGS. 5 and 6, the output speed reduction mechanism 100 includes a sun gear 202, a ring gear 204, a pinion 206 that meshes with the sun gear 202 and the ring gear 204, and a carrier 208 that rotatably supports the pinion 206. A planetary gear mechanism 200 is provided.

  A dog clutch 222 that can be connected to the output shaft 3 of the continuously variable transmission 1 is connected to the sun gear 202. A brake 224 that can prevent the carrier 208 from rotating is connected to the carrier 208.

  The differential gear DF is disposed in the housing 301 and includes a hollow outer member 302 connected to one end of the output shaft 3 (the end on the drive source ENG side in FIG. 5) via the dog clutch 222. The outer member 302 is rotatably supported by the housing 301 via bearings 303R and 303L. Further, seal members 303Ra and 303La for preventing the lubricating oil from flowing are provided on the side surfaces of the bearings 303R and 303L on the other axial side (the left side in FIGS. 5 and 6). Although the bearing 303L cannot be lubricated with the lubricating oil in the outer member 302, the sealing member prevents the lubricating oil from flowing to the side surface on one axial side (the right side in FIGS. 5 and 6) of the bearings 303R and 303L. 303Ra and 303La may be provided.

  An orthogonal shaft 304 that extends so as to be orthogonal to the axial direction of the output shaft 3 is provided inside the outer member 302. The connecting portion between the outer member 302 and the orthogonal shaft 304 is liquid-tightly sealed with a seal member 304a so that the lubricating oil in the outer member 302 does not leak outside.

  The orthogonal shaft 304 is provided with a pair of bevel gears 306 and 308 that are opposed to each other in the axial direction of the orthogonal shaft 304 and are rotatable about the orthogonal shaft 304. The differential gear DF includes a pair of side gears 310 and 312 that face each other and mesh with the pair of bevel gears 306 and 308.

  One side drive shaft 314 extending to one side (the drive source ENG side in the present embodiment) in the axial direction of the output shaft 3 is connected to one (right side of the drawing) side gear 310. The one side drive shaft 314 transmits power to the drive wheel on one side (right side in the drawing).

  The other (left side of the drawing) side gear 312 has a second drive shaft 316 extending through the hollow output shaft 3 and extending to the other axial direction of the output shaft 3 (in the present embodiment, the adjustment drive source 14 side). Connected. The other side drive shaft 316 transmits power to the driving wheel on the other side (left side in the drawing).

  The outer member 302 is connected to the ring gear 204 of the planetary gear mechanism 200 and the dog clutch 222 that can be connected to the output shaft 3 of the continuously variable transmission 1.

  With reference to FIGS. 6 and 7, output reduction mechanism 100 and differential gear DF are housed in housing 301. On the upper part of the inner surface of the housing 301, a flange 322 is provided for receiving the lubricating oil wound up by the rotation of the planetary gear mechanism 200. A through hole 324 is provided at a connection portion between the ring gear 204 and the outer member 302 so that the lubricating oil can easily enter the flange portion 322.

  Also, referring to FIGS. 6 to 8, the housing 301 has lubricating oil accumulated in the flange 322 at one side rather than a bearing 303 </ b> R located on one side (drive source ENG side) in the axial direction of the output shaft 3. A return oil passage 326 leading to an oil reservoir space 325 defined on the side (drive source ENG side) is provided. The return oil passage 326 is formed by utilizing the thick part of the casing 301, so that only the return oil path 326 has a larger power than the case where the casing 301 is thick. The transmission device can be reduced in size and weight.

  As shown in FIG. 8, the casing 301 is provided with a spiral groove 328 so as to be positioned at a portion where the one-side drive shaft 314 is inserted. By rotating the outer member 302 by the spiral groove 328, the lubricating oil in the oil reservoir space 325 is guided into the outer member 302.

  As shown in FIG. 9, the lubricating oil in the outer member 302 is supplied into a space in which the planetary gear mechanism 200 is disposed via a supply path 329 provided in the other side drive shaft 316. The lubricating oil supplied in the space where the planetary gear mechanism 200 is disposed is wound up by the rotation of the planetary gear mechanism 200. With reference to FIG. 7, a part of the rolled up lubricating oil is collected on the flange 322 by being transmitted along the inner peripheral surface of the outer member 302. Referring to FIG. 8, the lubricating oil collected in flange 322 is supplied to oil reservoir space 325 through return oil passage 326.

  According to the power transmission device of the present embodiment, the lubricating oil in the outer member 302 is supplied to the space where the planetary gear mechanism 200 is disposed via the supply path 329 provided in the other side drive shaft 316. Is done. Therefore, the supply of the lubricating oil to the space in which the planetary gear mechanism 200 is disposed is blocked until the amount of the lubricating oil in the outer member 302 reaches the supply path 329 provided in the other drive shaft 316. As a result, the amount of lubricating oil between the planetary gear mechanism 200 as the speed changing rotator and the differential gear DF can be maintained appropriately.

  In the present embodiment, the planetary gear mechanism 200 has been described as the speed change rotator, but the speed change rotator of the present invention is not limited to this. The speed change rotator of the present invention may be, for example, a dog clutch for applying engine braking.

  Moreover, in this embodiment, the input part 2 is comprised by the input edge part 2a and the cam disk 5, and the input part 2 is provided with the insertion hole 60 comprised by the through-hole 5a of the cam disk 5 continuing. Explained. However, the input portion of the present invention is not limited to this, for example, the input shaft is configured in a hollow shaft shape having an insertion hole so that one end is opened, and a through hole is formed so that the input shaft can be inserted into a disc-shaped cam disk. May be formed larger than that of the first embodiment, and the cam disk may be splined to the outer peripheral surface of the input shaft configured in a hollow shaft shape.

  In this case, the input shaft formed of a hollow shaft is provided with a notch hole corresponding to the notch hole of the cam disk. The pinion inserted into the input shaft meshes with the internal teeth of the rotating disk via the notch hole of the input shaft and the notch hole of the cam disk.

DESCRIPTION OF SYMBOLS 1 Continuously variable transmission 2 Input part 2a Input end part 3 Output shaft 4 Turning radius adjustment mechanism 5 Cam disk (cam part)
5a Through-hole 5b Notch hole 5c Integrated cam part 6 Rotating disk (rotating part)
6a Receiving hole (inner circumference)
6b Internal gear 8 Differential mechanism (Planetary gear mechanism)
14 Driving source for adjustment (electric motor)
15 Connecting rod 15a Large-diameter annular portion 15b Small-diameter annular portion 16 Connecting rod bearing 17 First one-way clutch 18 Oscillating link 18a Oscillating end 18b Projecting piece 18c Insertion hole 19 Connecting pin 20 Lever crank mechanism (four-bar linkage mechanism)
60 Insertion hole 70 Pinion 72 Pinion shaft 74 Bearing 80 Case 100 Output speed reduction mechanism 101 Input side sprocket 102 Output side sprocket 103 Chain 104 Second one-way clutch 105 Dog clutch 110 Accelerator opening degree detection part 111 Vehicle speed detection part 200 Planetary gear mechanism (for shifting) Rotating body)
202 Sun gear 204 Ring gear 206 Pinion 208 Carrier 222 Dog clutch 224 Brake 301 Housing 302 Outer member 303R, 303L Bearing 303Ra, 303La Seal member 304 Right angle shaft 304a Seal member (sealing member of the present invention)
306, 308 Bevel gears 310, 312 Side gear 314 One side drive shaft 316 The other side drive shaft 322 Gutter 324 Through hole 325 Oil reservoir space 326 Return oil path 328 Spiral groove 329 Supply path P1 Rotation center axis P2 Rotation center axis P3 Rotation of cam disk Disc center point Ra P1 and P2 distance Rb P2 and P3 distance R1 Eccentricity (P1 and P3 distance)
ENG Drive source for driving DF Differential gear

Claims (4)

A lubrication structure for a power transmission device comprising a differential gear arranged concentrically with an output shaft of a transmission,
The differential gear includes an outer member connected to one end of the output shaft, an orthogonal shaft provided in the outer member and extending orthogonally to the axial direction of the output shaft, A pair of bevel gears facing each other between the axial directions of the shafts and rotatably provided on the orthogonal shaft, and a pair of side gears facing each other and meshing with the pair of bevel gears,
One side gear is provided with a one-side drive shaft extending in one of the axial directions of the output shaft,
The other side gear is provided with the other side drive shaft that extends in the other axial direction of the output shaft and passes through the output shaft,
The output shaft is provided with a speed changing rotator,
Lubricating oil is stored in the outer member,
The lubricating oil in the outer member is supplied to the speed change rotating body via a supply path provided in the other drive shaft,
Lubricating oil scattered by the rotation of the speed change rotating body enters the outer member through a flange provided at the upper portion of the housing and a return oil passage that guides the lubricating oil received by the flange downward. A lubricating structure for a power transmission device, wherein the power transmission device is returned. A lubricating structure for a power transmission device according to claim 1,
The outer member and the orthogonal axis are configured separately.
A lubricating structure for a power transmission device, wherein a sealing member for preventing leakage of lubricating oil is provided at a connecting portion between the outer member and the orthogonal shaft. A lubricating structure for a power transmission device according to claim 1 or claim 2,
The transmission rotating body is a planetary gear mechanism having a sun gear or a ring gear and a carrier that rotatably and revolves a pinion that meshes with the sun gear or the ring gear. . A lubricating structure for a power transmission device according to any one of claims 1 to 3,
The outer member is pivotally supported on the housing via a pair of bearings,
The lubricating oil received by the flange is supplied to the oil reservoir space defined between the one bearing and the housing via the supply path.
The outer member or the one side drive shaft is provided with a spiral groove positioned between the outer member and the one side drive shaft,
Lubricating oil in the oil reservoir space is guided into the outer member by the spiral groove by rotation of the outer member or the one side drive shaft.