JP2007126999A - Lubrication structure of starting torque transmission mechanism of internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubrication structure capable of supplying a sufficient lubricating oil to a one-way clutch and a bearing without causing any problem of fuel economy and increasing the outer diameter of a constant-mesh starting torque transmission mechanism of an internal combustion engine using a one-way clutch. <P>SOLUTION: Radial grooves 30 are formed in a front end face 12c. Therefore, a centrifugal force is given to an engine oil to rapidly supply the large amount of engine oil to the ball bearing 18 and the one-way clutch 14. A peripheral groove 32 is formed in the outer peripheral surface 12b of a large diameter part 12, and connected to through holes 34 formed in the inner race 18a of the ball bearing 18. Therefore, the engine oil can be easily and surely supplied into the ball bearing 18. The engine oil is supplied from the ball bearing 18 also to the one-way clutch 14. Consequently, any problem of fuel economy does not occur since a hydraulic pressure does not need to be increased by increasing the size of a hydraulic pump. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a lubricating structure for an internal combustion engine starting rotational force transmission mechanism that transmits a rotational force in one direction by a starting motor to a rotational output shaft of an internal combustion engine through a one-way clutch and prevents transmission of a reverse rotational force. .

  In an internal combustion engine for a vehicle or the like, a configuration in which a pinion gear and a ring gear on the starter motor side are always meshed as an internal combustion engine starter torque transmission mechanism for transmitting the rotational force from the starter motor to the crankshaft. It is known (see, for example, Patent Document 1).

In such a constant mesh type internal combustion engine starting rotational force transmission mechanism, a one-way clutch is interposed between the ring gear and the crankshaft so that the rotational force of the ring gear when rotated in one direction by the starting motor. Is transmitted to the crankshaft via a one-way clutch. When the crankshaft is rotated by the output of the internal combustion engine, the one-way clutch is released so that the rotational force of the crankshaft is not transmitted to the ring gear side.
Japanese Patent No. 2970096 (page 3-4, FIG. 5-6)

  During operation of the internal combustion engine, the member is always in a sliding state in the one-way clutch portion. Therefore, a sufficient supply amount of lubricating oil to the one-way clutch is necessary during operation of the internal combustion engine. For this reason, in Patent Document 1, oil vanes are provided in the outer peripheral portion of the one-way clutch, the lubricating oil accumulated in the starter clutch chamber is scraped up, and the lubricating oil flows into the one-way clutch from the oil inlet.

  However, because the blades are specially protruded from the outer periphery of the one-way clutch in this way, the one-way clutch has an increased outer diameter and requires an oil sump in the design, so the starter mechanism has a larger diameter. Will do.

  When the ring gear is rotatably supported on the crankshaft via a bearing, the bearing is usually attached to a portion where the diameter of the crankshaft is increased. In such a case, providing a blade or an oil sump further outside invites further enlargement.

  In order to avoid such an increase in the diameter of the starter mechanism, a configuration in which lubricating oil is directly injected from the cylinder body side to a bearing or a one-way clutch can be considered. However, for this purpose, it is necessary to increase the hydraulic pressure by increasing the size of the pump, leading to unnecessary energy consumption, which is disadvantageous in terms of fuel consumption.

  The present invention does not increase the outer diameter of the constantly meshing internal combustion engine starting rotational force transmission mechanism using a one-way clutch, and can supply sufficient lubricating oil to the one-way clutch and bearing without causing a problem in terms of fuel consumption. The purpose is to realize a lubrication structure.

In the following, means for achieving the above object and its effects are described.
The internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 1 supports a ring gear via a bearing on an outer peripheral surface of a large diameter portion formed on an internal combustion engine rotation output shaft, and the ring gear and the internal combustion engine rotation output. By connecting the output shaft side member provided on the shaft via a one-way clutch disposed outside the outer peripheral surface of the large diameter portion, the one-way by the starting motor from the ring gear to the internal combustion engine rotation output shaft A lubricating structure in an internal combustion engine starting rotational force transmission mechanism that transmits rotational force and prevents reverse rotational force transmission, and is provided on an end face of the large-diameter portion facing the internal combustion engine main body, It has an outward movement promoting surface that applies a force toward the outer peripheral side of the large-diameter portion by rotation of an internal combustion engine rotation output shaft by contacting the lubricating oil flowing in from the engine body side Toss .

  By providing the outward movement promoting surface on the end surface facing the internal combustion engine main body side in the large-diameter portion in this way, the lubricating oil can be used without increasing the outer diameter of the internal combustion engine starting torque transmission mechanism. On the other hand, a force toward the outer peripheral side of the large-diameter portion can be applied during rotation of the internal combustion engine rotation output shaft. Therefore, a sufficient amount of lubricating oil can be supplied to the bearings of the ring gear disposed on the outer peripheral surface of the large diameter portion and the one-way clutch disposed on the outer side of the outer peripheral surface of the large diameter portion.

  In this way, when the lubricating oil comes into contact with the outward movement promoting surface that rotates around the rotation output shaft of the internal combustion engine, centrifugal force or pushing force is applied to the lubricating oil, and a force toward the outer peripheral side is applied to the lubricating oil. be able to. Therefore, there is no problem in terms of fuel consumption because it is not necessary to increase the hydraulic pressure by increasing the size of the pump.

  Thus, it is possible to supply sufficient lubricating oil to the one-way clutch and the bearing without increasing the outer diameter of the always-meshing internal combustion engine starting rotational force transmission mechanism using the one-way clutch and without causing a problem in fuel consumption.

  The internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 2 is characterized in that, in claim 1, the one-way clutch is in a state in which a portion of the ring gear supported by the bearing is sandwiched on the opposite side of the bearing. It is arranged with respect to the ring gear.

  With such a configuration, since the ring gear bearing and the one-way clutch can be arranged outside the outer peripheral surface of the large-diameter portion, the lubricating oil flowing from the end surface of the large-diameter portion toward the outer peripheral side is allowed to flow between the bearing and the one-way clutch. Can receive enough.

  In the internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 3, in claim 1 or 2, the bearing is a rolling bearing, and a through hole passing through an inner race of the bearing in a radial direction; An inner race inner circumferential surface and an outer circumferential surface of the large-diameter portion are formed on one or both surfaces, and provided with a circumferential groove that opens to at least the internal combustion engine body side and reaches the opening of the through hole. It is characterized by.

  Since the through-hole and the circumferential groove are formed in this way, a sufficient amount of the lubricating oil applied with the force toward the outer peripheral side of the large-diameter portion on the outward movement promoting surface is an opening of the circumferential groove. As a result, the lubricating oil flows in a large amount into the circumferential groove. Furthermore, since the circumferential groove reaches the opening of the through hole, the lubricating oil that has entered the circumferential groove can easily pass through the through hole and flow into the bearing.

As a result, more lubricating oil can be supplied to the bearing.
In the internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 4, in claim 3, the circumferential groove includes a circumferential groove that is formed in the circumferential direction and communicates with all the openings of the through holes. It is characterized by that.

  The circumferential groove is not only configured to open to the internal combustion engine main body side and reach the opening of the through hole, but also includes a circumferential groove formed in the circumferential direction and connecting all the openings of the through hole. It can be. As a result, especially when the peripheral groove is formed only on the outer peripheral surface of the large diameter portion, the opening of each through hole in the inner race of the bearing can be easily connected to the peripheral groove, and this lubrication The assembly workability of the internal combustion engine starting rotational force transmission mechanism having the structure is improved.

  In addition, even when the circumferential groove is formed only on the inner circumferential surface of the inner race of the bearing, the through hole is communicated with the circumferential groove, so that the lubricating oil can be interchanged between the through holes. There is no significant bias in the supply of lubricant to

Furthermore, even if the phase of the opening of the through hole and the circumferential groove is shifted after assembly, the lubricating oil supply capability can be maintained.
In the internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 5, in claim 3 or 4, between the ring gear and the output shaft side member, and between the ring gear and the internal combustion engine body, respectively. A ring-shaped seal member is disposed, and the inner edge of the ring gear is attached to the bearing on the inner peripheral surface side, and forms an inner race of the one-way clutch on the outer peripheral surface side and a through-hole that penetrates in the radial direction. The outer race of the bearing has a radial through hole communicating with the through hole of the inner race of the one-way clutch.

  In addition to the inner race of the bearing, the through holes are formed in the outer race of the bearing and the inner race of the one-way clutch. And both the through-holes of the outer race of a bearing and the inner race of a one-way clutch are connected.

  As a result, the lubricating oil supplied into the bearing can further pass through the through holes formed in the outer race of the bearing and the inner race of the one-way clutch, so that it can flow into the one-way clutch more easily.

Accordingly, more lubricating oil can be supplied to the one-way clutch.
In the internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 6, in claim 5, one or both of the inner peripheral surface of the inner race of the one-way clutch and the outer peripheral surface of the outer race of the bearing are provided with a peripheral surface. A circumferential groove formed in a direction and connecting all the openings of the through holes is formed.

  Thus, a circumferential groove is formed between the inner race of the one-way clutch and the outer race of the bearing so as to connect all the openings of the through holes. Accordingly, the through holes of the inner race of the one-way clutch and the outer race of the bearing can be easily connected to each other, and the assembling workability of the internal combustion engine starting rotational force transmission mechanism having this lubrication structure is improved.

Furthermore, even if the phase is shifted between the one-way clutch side through hole and the bearing side through hole after assembly, the lubricating oil supply capability can be maintained.
The internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 7 supports a ring gear via a bearing on an outer peripheral surface of a large diameter portion formed on an internal combustion engine rotation output shaft, and the ring gear and the internal combustion engine rotation output. By connecting the output shaft side member provided on the shaft via a one-way clutch disposed outside the outer peripheral surface of the large diameter portion, the one-way by the starting motor from the ring gear to the internal combustion engine rotation output shaft A lubrication structure in an internal combustion engine starting rotational force transmission mechanism that transmits rotational force and prevents reverse rotational force from being transmitted, and is one of an inner peripheral surface of an inner race of the bearing and an outer peripheral surface of the large-diameter portion. Or a circumferential groove formed on both surfaces and opening on both the internal combustion engine main body side and the opposite side of the internal combustion engine main body, and an end surface of the large diameter portion facing the internal combustion engine main body side. Internal combustion engine body And an outward movement promoting surface for applying a force toward the outer peripheral side of the large-diameter portion by rotation of an internal combustion engine rotation output shaft by contacting the lubricating oil flowing in from .

  In this way, the end face facing the internal combustion engine main body at the large diameter portion is provided with the outward movement promoting surface, so that the lubricating oil can be injected into the internal combustion engine without increasing the outer diameter of the internal combustion engine starting torque transmission mechanism. A force toward the outer peripheral side of the large-diameter portion can be applied during rotation of the engine rotation output shaft. Therefore, a sufficient amount of lubricating oil can be supplied to the bearings of the ring gear disposed on the outer peripheral surface of the large diameter portion and the one-way clutch disposed on the outer side of the outer peripheral surface of the large diameter portion.

  In this way, when the lubricating oil comes into contact with the outward movement promoting surface that rotates around the rotation output shaft of the internal combustion engine, centrifugal force or pushing force is applied to the lubricating oil, and a force toward the outer peripheral side is applied to the lubricating oil. Therefore, there is no problem in terms of fuel consumption because there is no need to increase the hydraulic pressure by increasing the size of the pump.

  In addition, the circumferential groove opens on both the internal combustion engine body side and the opposite side. For this reason, even if lubricating oil is supplied from the internal combustion engine main body side of the large diameter portion, it can be supplied to the side opposite to the internal combustion engine main body side through the circumferential groove. As a result, lubricating oil can be supplied from both sides of the bearing, and the bearing and the one-way clutch can be more reliably lubricated.

  Thus, it is possible to supply sufficient lubricating oil to the one-way clutch and the bearing without increasing the outer diameter of the always-meshing internal combustion engine starting rotational force transmission mechanism using the one-way clutch and without causing a problem in fuel consumption.

  In the internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 8, in any one of claims 3 to 7, the outward movement promoting surface is radiating from the rotation center side to the outer peripheral side on the end surface of the large diameter portion. It is formed as the side surface of the radial groove | channel or radial protrusion formed in this.

  Thus, by forming the outward movement promoting surface as the side surface of the radial groove or the radial protrusion, the lubricating oil contacting the end surface of the large diameter portion is rotated with the rotation of the rotation output shaft of the internal combustion engine. Can do. As a result, a force toward the outer peripheral side of the large diameter portion can be applied to the lubricating oil as a centrifugal force.

  In the internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 9, when the outward movement promoting surface is formed as a side surface of the radial groove in claim 8, the outer peripheral side end of the radial groove is And reaching the opening of the circumferential groove.

  Since the outer circumferential end of the radial groove reaches the opening of the circumferential groove, the lubricating oil can be reliably guided to the circumferential groove, and more sufficient lubricating oil is supplied to the one-way clutch and bearing more reliably. it can.

  The internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 10, wherein the radial groove is wider than the opening of the peripheral groove on the rotation center side and the peripheral groove on the outer peripheral side. It is characterized by being close to the opening width.

As a result, more lubricating oil can be concentrated in the circumferential groove, and more lubricating oil can be supplied to the one-way clutch and the bearing.
In the internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 11, in claim 8, a plurality of the radial grooves or radial protrusions form a set, and each set of the radial grooves or The arrangement width of the radial ridge is wider than the opening of the circumferential groove, and the outer circumferential side is close to the opening width of the circumferential groove.

  By arranging a plurality of radial grooves or radial protrusions as described above as described above, more lubricating oil can be concentrated in the circumferential groove, and more lubricating oil can be concentrated in the one-way clutch or bearing. Can supply.

  In the internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 12, when the outward movement promoting surface is formed as a side surface of the radial groove in claim 8, the radial groove is a circumferential groove. It is characterized by being gradually deepened toward the opening.

  In this way, the radial groove is deep at the opening position of the circumferential groove, and the radial groove and the circumferential groove are connected to each other at a wider portion in the depth direction, so that more lubricating oil is removed from the radial groove. It is difficult to overflow and can be concentrated in the circumferential groove, and more lubricating oil can be supplied to the one-way clutch and the bearing.

  The internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 13 is the lubricating structure according to claim 1 or 2, wherein the outward movement promoting surface is radially formed on the end surface of the large-diameter portion from the rotation center side to the outer peripheral side. It is formed as a side surface of a radial groove or a radial protrusion.

  Thus, by forming the outward movement promoting surface as the side surface of the radial groove or the radial protrusion, the lubricating oil contacting the end surface of the large diameter portion is rotated with the rotation of the rotation output shaft of the internal combustion engine. Can do. As a result, a force toward the outer peripheral side of the large diameter portion can be applied to the lubricating oil as a centrifugal force.

  In the internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 14, in claim 13, the bearing is a rolling bearing, and an inner race of the bearing is provided with a through hole penetrating in a radial direction. An outward movement promoting surface is formed as a side surface of the radial groove, and the radial groove reaches the through hole by being gradually deepened toward the outer peripheral side of the large diameter portion. To do.

In this way, by gradually deepening the radial groove and reaching the through hole in the inner race of the bearing, the lubricating oil can be directly supplied from the radial groove to the through hole without providing the peripheral groove.
In the internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 15, in any one of claims 1 to 14, the output shaft side member covers a side opposite to the internal combustion engine main body side with respect to the bearing. The surface of the output shaft side member on the bearing side of the output shaft side member forms a fin for extruding lubricating oil from the rotation center side to the outer peripheral side.

  By forming the fin on the bearing side surface of the output shaft side member in this way, the lubricating oil flowing out from the bearing side can be pushed out to the outer peripheral side as the internal combustion engine rotation output shaft rotates. Thereby, sufficient lubricating oil can be more reliably supplied to the one-way clutch on the outer peripheral side of the output shaft side member.

An internal combustion engine starting rotational force transmission mechanism lubricating structure according to a sixteenth aspect is characterized in that, in the fifteenth aspect, an oil-repellent surface treatment is applied to the surface of the fin.
By performing the oil-repellent surface treatment in this way, it is possible to prevent the lubricating oil from adhering to the fin and causing flow resistance when the lubricating oil moves toward the outer peripheral side by the fin. As a result, the lubricating oil can be guided to the one-way clutch more quickly, and sufficient lubricating oil can be supplied to the one-way clutch more reliably.

  An internal combustion engine starting rotational force transmission mechanism lubricating structure according to claim 17 is the lubricating structure according to any one of claims 1 to 16, wherein at least the outward movement promoting surface of the end surface of the large-diameter portion is subjected to an oil-repellent surface treatment. It is characterized by.

  By performing the oil-repellent surface treatment in this way, when the lubricating oil is directed to the outer peripheral side of the large diameter portion by centrifugal force or pushing force on the outward movement promoting surface, the lubricating oil adheres to the outward movement promoting surface. Thus, the occurrence of flow resistance can be suppressed. As a result, the lubricating oil can be guided to the outer peripheral side more quickly, and sufficient lubricating oil can be supplied to the bearing and the one-way clutch more reliably.

[Embodiment 1]
FIG. 1 shows an internal combustion engine starting rotational force transmission mechanism of an internal combustion engine for a vehicle, and shows a longitudinal sectional view around the rear side of the internal combustion engine that outputs to the clutch or torque converter side. In FIG. 1, the upper half of the rotation axis C, which is the central axis, is shown, and only the cut surface is shown except for the cylinder block 2 and the crankshaft 4 (corresponding to the internal combustion engine rotation output shaft).

  A journal bearing portion is constituted by the cylinder block 2 and the ladder beam, and the crankshaft 4 is supported by the cylinder block 2 so as to be rotatable at a portion of the journal 4a. Thus, the crankshaft 4 is arranged in a state where the rear end portion protrudes from the lower rear portion of the cylinder block 2. A flywheel (or drive plate) 6, an outer race support plate 8 (corresponding to an output shaft side member), and a ring gear 10 are attached to the rear end portion of the crankshaft 4.

  The outer race support plate 8, which shows the upper half in FIG. 1, is formed in a circular flat plate shape with an opening at the center, and together with the flywheel (or drive plate) 6, the crankshaft 4 at the periphery of the center opening. The large-diameter portion 12 is fixed to the rear end surface 12a by bolt fastening. Accordingly, the outer race support plate 8 is configured to rotate in conjunction with the crankshaft 4 together with the flywheel (or drive plate) 6.

  The ring gear 10 whose upper half is shown in FIG. 1 is a disc having a central portion that is largely open to form an inner edge portion and a bent portion 10a in the radial direction. An inner race 16 of the one-way clutch 14 is formed in the inner edge portion in a flange shape, and a gear portion 10b is provided in a ring shape on the outer peripheral portion. The ring gear 10 is formed on the crankshaft 4 via a rolling bearing, here a ball bearing 18, on the side opposite to the one-way clutch 14, that is, on the center side (rotation shaft C side), in the inner race 16. It is attached to the outer periphery of the large diameter portion 12. Therefore, when the one-way clutch 14 is in the released state, the ring gear 10 can freely rotate independently of the rotation of the crankshaft 4.

  The ball bearing 18 is attached to the outer peripheral surface 12b of the large-diameter portion 12 by press-fitting with an inner race 18a. The inner race 16 of the one-way clutch 14 is fitted to the outer periphery of the outer race 18b of the ball bearing 18 so as to be in contact with the thrust bearing portion 18c.

  The gear portion 10b of the ring gear 10 is always meshed with the pinion gear of the starter motor below the crankshaft 4, and the ring gear 10 rotates by receiving a rotational force from the starter motor via the pinion gear.

  An outer race 20 is provided on the outer peripheral portion of the outer race support plate 8 so as to face the inner race 16 formed in the center opening portion of the ring gear 10. A cage 14b having sprags 14a is disposed between the inner race 16 and the outer race 20, so that a one-way clutch 14 is configured between the ring gear 10 and the outer race support plate 8. Therefore, in the inner race 16, the ball bearing 18 is disposed on the inner peripheral surface 16a side, and the one-way clutch 14 is configured on the outer peripheral surface 16b side opposite to the inner peripheral surface 16a. As a result, both the ball bearing 18 and the one-way clutch 14 exist outside the outer peripheral surface 12 b of the large-diameter portion 12.

  The one-way clutch 14 configured as described above connects the outer race support plate 8 and the ring gear 10 when rotating in one direction to transmit the torque of the starting motor from the ring gear 10 side to the outer race support plate 8. Engage state. As a result, the crankshaft 4 can be rotated by the output of the starting motor.

  When the rotation of the outer race support plate 8 interlocked with the crankshaft 4 by the output of the internal combustion engine becomes faster than the rotation of the ring gear 10 by the output of the starter motor by starting the operation of the internal combustion engine, the rotation of the ring gear 10 is The rotation is in the opposite direction relative to the race support plate 8. For this reason, the one-way clutch 14 is in a disengaged state, and the starter motor can be stopped after the internal combustion engine is started even when the pinion gear and the ring gear 10 are always meshed.

  In order to lubricate the ball bearing 18 and the one-way clutch 14, engine oil as lubricating oil is supplied through an oil passage 22 in the cylinder block 2 as shown by the arrow in the figure. In order to prevent leakage of the engine oil, a first oil seal member 24 as a ring-shaped seal member is disposed between the outer race support plate 8 and the bent portion 10 a of the ring gear 10. The first oil seal member 24 is fixed to the ring gear 10 side by being fitted to the inner peripheral surface of the bent portion 10a. As a result, the main seal lip 24 a and the sub seal lip 24 b as seal portions formed on the inner peripheral side of the first oil seal member 24 slide on the seal sliding surface 20 a that is the outer peripheral surface of the outer race 20. Contact is possible. Thus, the first oil seal member 24 performs an oil seal between the outer race support plate 8 and the ring gear 10. Further, a second oil seal member 26 having a larger diameter than the first oil seal member 24 is arranged as a ring-shaped seal member on the opposite side (outside) of the first oil seal member 24 across the bent portion 10a. Yes. The second oil seal member 26 is mainly on the inner peripheral surface of the arc-shaped seal fitting portion 2a of the cylinder block 2 above the crankshaft 4 and mainly inside the rear end of the oil pan below the crankshaft 4. By being fitted to the peripheral surface, it is fixed at the illustrated position. Thus, the main seal lip 26a and the sub seal lip 26b, which are two seal portions formed on the inner peripheral side of the second oil seal member 26, are slidably in contact with the outer peripheral surface of the bent portion 10a. Yes. Thus, the oil seal between the ring gear 10 and the internal combustion engine body (cylinder block 2 and oil pan) is executed.

  Here, the large-diameter portion 12 of the crankshaft 4 is shown in FIG. 2A is a front view and FIG. 2B is a perspective view. As shown in the drawing, eight radial grooves 30 arranged radially in a state of converging at the center of rotation are provided on the front end surface 12c facing the cylinder block 2 side at equal phase (here 45 °) intervals. ing. Further, a circumferential groove 32 continuing to the eight radial grooves 30 is formed to the middle of the outer circumferential surface 12 b of the large diameter portion 12.

  An inner race 18a of the ball bearing 18 fitted to the large diameter portion 12 is shown in FIG. 3A is a front view, FIG. 3B is a right side view, and FIG. 3C is a perspective view. As shown in the figure, eight through holes 34 are provided in the center in the axial direction at equal phase (here, 45 °) intervals. As shown in FIG. 4, when the ball bearing 18 is fitted to the large diameter portion 12, the phase is adjusted so that each through hole 34 of the inner race 18 a is connected to the circumferential groove 32 of the large diameter portion 12. Has been. 4A is a front view, and FIG. 4B is a perspective view.

Thereby, as shown in FIG. 1, the radial groove 30, the circumferential groove 32, and the through hole 34 are formed as a continuous passage.
Here, during operation of the internal combustion engine, the engine oil from the oil passage 22 flows between the cylinder block 2 and the large diameter portion 12 as indicated by an arrow. As a result, the engine oil comes into contact with the front end surface 12 c of the large diameter portion 12 and flows into the end portion on the axial center side of the radial groove 30.

  At this time, since the radial shaft 30 is also rotated due to the rotation of the crankshaft 4, the side surface 30a of the radial groove 30 comes into contact with the engine oil to forcibly rotate the engine oil. Furthermore, the engine oil that falls into the radial grooves 30 due to the rotation of the radial grooves 30 also increases.

  A centrifugal force acts on the rotating engine oil, and a force directed toward the outer peripheral surface 12b of the large diameter portion 12 is applied. Therefore, the engine oil that has flowed through the radial groove 30 as shown in the figure is concentrated in the opening 32 a of the circumferential groove 32. The engine oil is pushed into the circumferential groove 32 by this concentration. The engine oil flows through the circumferential groove 32 and reaches the opening 34a of the through hole 34, and further passes through the through hole 34 by centrifugal force. As a result, it flows into the ball bearing 18, here between the two balls 18 d. In addition, since the oil in the circumferential groove 32 is sucked by the movement of the engine oil in the through hole 34, a larger amount of engine oil is quickly sucked from the radial groove 30 side and quickly into the ball bearing 18. Will be supplied.

  The engine oil flowing into the ball bearing 18 overflows from between the inner race 18a and the outer race 18b, contacts the outer race support plate 8, and is further subjected to centrifugal force by the rotation of the outer race support plate 8. A large amount and quickly supplied to the one-way clutch 14 side.

According to the first embodiment described above, the following effects can be obtained.
(I). A radial groove 30 is formed in the front end surface 12c, which is the end surface of the large-diameter portion 12 on the internal combustion engine body side, so that centrifugal force is applied to the engine oil supplied from the internal combustion engine body side, Giving the power to go. Thus, a large amount of engine oil can be quickly supplied to the outer peripheral side where the ball bearing 18 and the one-way clutch 14 are present.

  Further, a circumferential groove 32 is formed on the outer circumferential surface 12 b of the large diameter portion 12, and this circumferential groove 32 is connected to the opening 34 a of each through hole 34 formed in the inner race 18 a of the ball bearing 18. Therefore, the engine oil can be supplied in a large amount and quickly into the ball bearing 18 easily and reliably.

  Since the engine oil overflowing from the ball bearing 18 is also supplied to the one-way clutch 14, a large amount of engine oil can be supplied to the one-way clutch 14 quickly.

  Thus, the radial groove 30 having the side surface 30a as the outward movement promoting surface is provided on the front end surface 12c in the large diameter portion 12, so that the outer diameter of the internal combustion engine starting rotational force transmission mechanism is not increased. The engine oil can be given a force toward the outer peripheral side of the large diameter portion 12 when the crankshaft 4 rotates.

Further, since the engine oil can be supplied by the force applied in this way, there is no problem in terms of fuel consumption because it is not necessary to increase the hydraulic pressure by increasing the size of the hydraulic pump.
In this way, sufficient engine oil can be supplied to the one-way clutch 14 and the ball bearing 18 without increasing the outer diameter of the always-meshing internal combustion engine starting rotational force transmission mechanism using the one-way clutch 14 and with no problem in fuel consumption. .

[Embodiment 2]
The present embodiment is different from the first embodiment in that a crankshaft 104 having a large diameter portion 112 shown in FIG. 5 is used instead of the large diameter portion 12 shown in FIG. 5A is a plan view and FIG. 5B is a perspective view. The other configuration is the same as that of the first embodiment.

  In the large-diameter portion 112, a circumferential groove 136 is formed on the outer peripheral surface 112b so as to cross the tip portion of the peripheral groove 132 so that the grooves communicate with each other. Is different. Accordingly, as shown in FIG. 6, when the inner race 118a (the same shape as the inner race 18a shown in FIG. 3) is fitted to the outer peripheral surface 112b of the large diameter portion 112, a through hole formed in the inner race 118a is formed. The opening of 134 is located in the circumferential groove 136. Accordingly, the circumferential groove 136 is in a state of connecting all the openings of the through hole 134. 6A is a plan view and FIG. 6B is a perspective view.

  Therefore, when the ball bearing is fitted to the large diameter portion 112, the opening of the through hole 134 is positioned to the circumferential groove 136 without considering the phase around the axis of the inner race 118 a with respect to the large diameter portion 112. When the ball bearing is fitted in the axial direction, the through hole 134 and the circumferential groove 132 are connected by the circumferential groove 136.

According to the second embodiment described above, the following effects can be obtained.
(I). The effect of the first embodiment is produced.
(B). As described above, since the circumferential groove 136 is formed on the outer peripheral surface 112b of the large-diameter portion 112 so as to communicate all the openings of each through-hole 134, the opening of each through-hole 134 in the inner race 118a of the ball bearing is formed. Thus, it can be easily connected to the circumferential groove 132, and the assembly workability of the internal combustion engine starting rotational force transmission mechanism is improved.

Further, even if the inner race 118a and the large diameter portion 112 are out of phase after fitting, the engine oil supply capability is maintained.
[Embodiment 3]
In the present embodiment, as shown in the longitudinal sectional view of the main part of FIG. 7, in addition to the configuration of either the first embodiment or the second embodiment, a radial through hole is further provided in the outer race 218b of the ball bearing. 238 is formed. A radial through hole 240 is formed in the same phase in the inner race 216 of the one-way clutch 214 formed in the ring gear 210 so as to be continuous with the radial through hole 238. Other configurations are the same as those of the first embodiment or the second embodiment.

  The engine oil that has flowed into the ball bearing 218 from the through-hole 234 provided in the inner race 218a of the ball bearing 218 flows out between the inner race 218a and the outer race 218b in the same manner as in the first and second embodiments. It is. However, in the present embodiment, separately from this, the one-way clutch is also provided on the route via the through-hole 238 formed in the outer race 218b of the ball bearing 218 and the through-hole 240 formed in the inner race 216 of the one-way clutch 214. 214.

According to the third embodiment described above, the following effects can be obtained.
(I). The effects of the first or second embodiment are produced.
(B). As described above, the outer race 218 b of the ball bearing 218 and the inner race 216 of the one-way clutch 214 are also provided with through holes 238 and 240. For this reason, the engine oil supplied into the ball bearing 218 can flow into the one-way clutch 214 more easily by passing through the through holes 238 and 240. Therefore, more engine oil can be supplied to the one-way clutch 214 as well.

[Embodiment 4]
In the present embodiment, as shown in the longitudinal sectional view of the main part of FIG. 8, the circumferential groove that communicates each through hole 340 with the inner peripheral surface 316 a of the inner race 316 of the one-way clutch 314 formed on the inner peripheral side of the ring gear 310. The point where 316b is formed is different from the configuration of the third embodiment. Other configurations are the same as those of the third embodiment.

  With this configuration, the circumferential groove 316b allows the through-hole 338 formed in the outer race 318b of the ball bearing 318 and the through-hole 340 formed in the inner race 316 of the one-way clutch 314 to be in phase with each other. These through holes 338 and 340 can communicate with each other.

  As shown in the longitudinal sectional view of the main part of FIG. 9, not only the inner race 316 side of the one-way clutch 314 but the outer circumferential surface 319 of the outer race 318b of the ball bearing 318 is formed with a circumferential groove 319a that communicates each through hole 338. It is possible to have a similar function.

According to the fourth embodiment described above, the following effects can be obtained.
(I). The effect of the third embodiment is produced.
(B). As described above, the circumferential groove 316b that communicates each through hole 340 with the inner circumferential surface 316a of the inner race 316 of the one-way clutch 314, or the circumference that communicates each through hole 338 with the outer circumferential surface 319 of the outer race 318b of the ball bearing 318. Directional grooves 319a are formed. Therefore, the opening of the through-hole 338 provided in the outer race 318b of the ball bearing 318 can be easily connected to the through-hole 340 provided in the inner race 316 of the one-way clutch 314, and the internal combustion engine start torque transmission mechanism Assembling workability is improved.

Further, even if the outer race 318b and the inner race 316 are out of phase after assembly, the engine oil supply capability is maintained.
[Embodiment 5]
In the present embodiment, as shown in the longitudinal sectional view of the main part of FIG. 10, the radial grooves 430 are formed on the front end surface 412c of the large diameter portion 412 as in the first embodiment, but the large diameter portion 412 is formed. The peripheral surface groove 432 formed in the outer peripheral surface 412b is open on the opposite side of the cylinder block 402 side as well. Further, the inner race 418a of the ball bearing 418 is not formed with a radial through hole. The other configuration is the same as that of the first embodiment.

  Here, during operation of the internal combustion engine, the engine oil discharged from the oil passage 422 in the cylinder block 402 contacts the front end surface 412c of the large diameter portion 412 and flows into the end portion of the radial groove 430 on the shaft center side. Further, the engine oil that has not flowed directly into the radial groove 430 is caused to fall into the radial groove 430 by the rotation of the radial groove 430. With this rotation, the side surface 430a of the radial groove 430 comes into contact with the engine oil to forcibly rotate the engine oil in the radial groove 430. As a result, centrifugal force acts on the engine oil, and a force directed toward the outer peripheral surface 412b of the large diameter portion 412 is applied to the engine oil. The engine oil that has flowed through the radial grooves 430 as indicated by the arrows is concentrated in the opening 432a of the circumferential groove 432. Therefore, engine oil is pushed into the circumferential groove 432, flows from the opposite opening 432b to the outer race support plate 408 side, and contacts the inner surface 408a of the outer race support plate 408. Since the outer race support plate 408 also rotates together with the crankshaft 4, the engine oil that has flowed between the inner surface 408a and the inner race 418a of the ball bearing 418 as it is by centrifugal force is applied to the ball bearing 418 and the one-way clutch 414, respectively. Supplied. The engine oil that has flowed through the radial grooves 430 is also supplied to the ball bearings 418 from the cylinder block 402 side.

  The function similar to that of the circumferential groove 432 is the same as that of the cylinder block 402 side in accordance with the phase of the radial groove 430 on the inner circumferential surface 418c of the inner race 418a of the ball bearing 418, as shown in the longitudinal sectional view of the main part in FIG. This can also be realized by forming a circumferential groove 419 that is open on both sides of the opposite side.

According to the fifth embodiment described above, the following effects can be obtained.
(I). A radial groove 430 is formed on the front end surface 412c, which is the end surface of the large-diameter portion 412 on the internal combustion engine body side, so that centrifugal force is applied to the engine oil supplied from the internal combustion engine body side, The power to go to can be given. Thus, a large amount of engine oil can be quickly supplied to the outer peripheral side where the ball bearing 418 and the one-way clutch 414 exist.

  Moreover, the circumferential grooves 432 and 419 are opened on both sides of the cylinder block 402 side and the opposite side. For this reason, even if engine oil is supplied from the cylinder block 402 side, it passes through the circumferential grooves 432 and 419 and is also supplied to the side opposite to the cylinder block 402 side. As a result, the engine oil is allowed to flow from both sides of the ball bearing 418, so that a large amount of engine oil is supplied to the ball bearing 418 quickly and reliably.

  10 and 11, the engine oil supply to the one-way clutch 414 may be supplied through a hole opened in the middle of the ring gear 410, but it is supplied from the side opposite to the cylinder block 402. Cheap. Therefore, a large amount of engine oil can be supplied to the one-way clutch 414 reliably and quickly. Therefore, it is not necessary to increase the hydraulic pressure by increasing the size of the pump.

  In this way, the one-way clutch 414 and the ball bearing 418 are supplied with sufficient engine oil without increasing the outer diameter of the always-meshing internal combustion engine starting rotational force transmission mechanism using the one-way clutch 414 and without causing problems in terms of fuel consumption. Can supply.

[Embodiment 6]
In the large diameter portion 512 of the present embodiment, as shown in FIG. 12, the radial groove 530 is wide on the rotating shaft side, and gradually becomes narrower as the outer peripheral surface 512b is approached. 12A is a plan view, FIG. 12B is a front view, and FIG. 12C is a perspective view. Except for the radial groove 530, the configuration is the same as that of the first embodiment.

According to the sixth embodiment described above, the following effects can be obtained.
(I). In addition to the effects of the first embodiment, the probability that the engine oil directly contacts the wide radial groove 530 on the rotating shaft side of the front end surface 512c with which the engine oil first contacts is increased. For this reason, a larger amount of engine oil is more likely to be concentrated in the circumferential groove 532 due to the centrifugal force and induction by the side surface 530 a of the radial groove 530.

  In this way, the constantly meshing internal combustion engine starting rotational force transmission mechanism using the one-way clutch can be supplied to the one-way clutch and the ball bearing without increasing the outer diameter and with no problem in fuel consumption.

[Embodiment 7]
In the large-diameter portion 612 of this embodiment, the radial groove 630 is as shallow as shown in FIG. 1 on the center side as shown in the longitudinal sectional view of the main part in FIG. 13, but gradually becomes deeper as it approaches the outer peripheral surface 612b. The depth is the same as the length of the circumferential groove 32 shown in FIG. As a result, the radial groove 630 also serves as a circumferential groove.

  Moreover, since the radial grooves 630 are gradually formed deeper, a larger amount of engine oil can be accommodated as the outer peripheral surface 612b is approached. At the same time, since the area of the side surface 630a is extremely large, centrifugal force due to rotation of the crankshaft 604 can be effectively applied to the large amount of engine oil.

According to the seventh embodiment described above, the following effects can be obtained.
(I). While the effects of the first embodiment are produced and the centrifugal force can be effectively applied to a large amount of engine oil as described above, a larger amount of engine oil is formed in the inner race 618a of the ball bearing 618. It becomes easy to concentrate on the through hole 634.

  In this way, the outer diameter of the constantly meshing internal combustion engine starting rotational force transmission mechanism using the one-way clutch 614 is not increased in size and there is no problem in fuel consumption, and a larger amount of engine oil is supplied to the one-way clutch 614 and the ball bearing 618. it can.

[Other embodiments]
(A). Instead of the wide radial groove 530 in the sixth embodiment, the front end surface 712c of the large-diameter portion 712 has one set of a plurality of (three in the figure), although the width does not change, as shown in FIG. The radial grooves 730a, 730b, and 730c are arranged. 14A is a plan view, FIG. 14B is a front view, and FIG. 14C is a perspective view. The arrangement width of the radial grooves 730 a, 730 b, and 730 c of each set is wider than the opening of the peripheral groove 732 on the center side. And on the outer peripheral surface 712 b side, the opening width of the peripheral groove 732 is made closer. Here, the pair of radial grooves 730 a, 730 b, and 730 c are gathered to the same width as the opening width of the circumferential groove 732 and are continuous with the circumferential groove 732.

  As a result, the engine oil that has flowed into the radial grooves 730 a, 730 b, and 730 c on the center side when the crankshaft 704 is rotated gathers in one circumferential groove 732. This produces an effect similar to that of the sixth embodiment.

In FIG. 14, three sets of radial grooves 730a, 730b, and 730c are provided, but two or four or more may be provided.
(B). In Embodiments 1, 3, 4, 6 and FIG. 14 described above, the peripheral groove is formed on the outer peripheral surface of the large diameter portion, but may be formed on the inner peripheral surface of the inner race of the ball bearing. Or you may form in both the outer peripheral surface of a large diameter part, and the inner peripheral surface of the inner race of a ball bearing.

  The circumferential groove and circumferential groove of the second embodiment may also be formed on the inner circumferential surface of the inner race of the ball bearing, and the outer circumferential surface of the large diameter portion and the inner circumferential surface of the inner race of the ball bearing. You may form in both.

  (C). In place of the radial grooves of the first, second, third, fourth, and fifth embodiments, radial ridges may be provided on the front end surface of the large diameter portion. For example, as shown in FIG. 15, the radial ridges 830 may be radially arranged on the front end surface 812c of the large diameter portion 812 from the center side to the outer peripheral surface 812b. 15A is a plan view, FIG. 15B is a front view, and FIG. 15C is a perspective view.

  Here, assuming that the crankshaft 804 is rotating as shown in the figure, the tip of the radial ridge 830 is adjacent to the circumferential groove 832 provided on the outer circumferential surface 812b on the side opposite to the rotational direction. Present in phase.

  As a result, the side surface 830a of the radial protrusion 830 functions as an outward movement promoting surface and comes into contact with the engine oil flowing in from the cylinder block side, so that the outer periphery of the large-diameter portion 812 is rotated by the rotation of the crankshaft 804. A force toward the surface 812b is applied.

  As shown in FIG. 16, a plurality of radial protrusions 930 a and 930 b, here two in pairs, are provided on the front end surface 912 c of the large-diameter portion 912, and the arrangement width on the center side is wider than the width of the circumferential groove 932. The outer peripheral surface 912b may be disposed so as to approach the width of the peripheral groove 932. 16A is a plan view, FIG. 16B is a front view, and FIG. 16C is a perspective view. Also by this, the side surfaces of the radial protrusions 930a and 930b give a force toward the outer peripheral surface 912b by centrifugal force to the engine oil, and are guided and concentrated in the peripheral groove 932.

  As a result, a large amount of engine oil is concentrated in the opening of the circumferential groove 932, so that the outer diameter of the constantly meshing internal combustion engine starting rotational force transmission mechanism using the one-way clutch is not increased and there is a problem in terms of fuel consumption. And a larger amount of engine oil can be supplied to one-way clutches and ball bearings.

  (D). As shown in the perspective view of FIG. 17 and the vertical cross-sectional view of the main part of FIG. 18, the outer race support plate 958 may be provided with fins 959 on the surface (inner surface) 958a on the ball bearing 968 side. By providing the fins 959 in this way, the engine oil flowing out from the ball bearings 968 is positively pushed out by the one-way clutch 964 side as shown by the arrows by the fins 959 that rotate as the crankshaft 954 rotates.

  18 shows an example in which the outer race support plate 958 of FIG. 17 is combined with the configuration of the first embodiment, but the outer race support plate 958 of FIG. 17 may be combined with another embodiment.

As a result, the effects of the respective embodiments become more remarkable.
(E). In each of the above embodiments, an oil-repellent surface treatment may be applied to the inner surface of each radial groove so that the engine oil that has entered the radial groove is supplied to the outer peripheral surface side more quickly. This reduces the flow resistance of the engine oil due to viscosity in the radial grooves. For this reason, it is possible to supply a larger amount of engine oil to the one-way clutch and the ball bearing without increasing the outer diameter of the always-meshing internal combustion engine starting rotational force transmission mechanism using the one-way clutch and without causing a problem in fuel consumption.

  Further, an oil repellent surface treatment may be applied to the inner surface of each circumferential groove, the inner surface of each circumferential groove, the inner surface of each through hole, the side surface of each radial protrusion, and the surface of each fin. As a result, the fluidity of the engine oil is further increased, and the above-described effect becomes remarkable.

(F). The configuration in which the radial grooves are deepened on the outer peripheral side as in the seventh embodiment may be applied to the radial grooves in the second, third, fourth, fifth and sixth embodiments and FIG.
(G). In each of the above embodiments, a ball bearing is used as the rolling bearing, but a roller bearing may be used.

FIG. 2 is a longitudinal sectional view of an internal combustion engine starting rotational force transmission mechanism used in the vehicle internal combustion engine of the first embodiment. FIG. 3 is an explanatory diagram showing a configuration of a large diameter portion of the crankshaft of the first embodiment. FIG. 3 is an explanatory diagram illustrating a configuration of an inner race of the ball bearing according to the first embodiment. Explanatory drawing which shows the state which attached the ball bearing to the large diameter part of the crankshaft of Embodiment 1. FIG. Explanatory drawing which shows the structure of the large diameter part of the crankshaft of Embodiment 2. FIG. Explanatory drawing which shows the relationship between the inner race of a ball bearing at the time of attaching a ball bearing to the large diameter part of a crankshaft, and a large diameter part in Embodiment 2. FIG. FIG. 6 is a longitudinal sectional view of a main part of an internal combustion engine starting rotational force transmission mechanism according to a third embodiment. FIG. 10 is a longitudinal sectional view of a main part of an internal combustion engine starting rotational force transmission mechanism according to a fourth embodiment. FIG. 10 is a longitudinal sectional view of an essential part of a modification of the internal combustion engine starting rotational force transmission mechanism according to the fourth embodiment. FIG. 10 is a longitudinal sectional view of a main part of an internal combustion engine starting rotational force transmission mechanism according to a fifth embodiment. FIG. 10 is a longitudinal sectional view of an essential part of a modification of the internal combustion engine starting rotational force transmission mechanism according to the fifth embodiment. Explanatory drawing which shows the structure of the large diameter part of the crankshaft of Embodiment 6. FIG. FIG. 10 is a longitudinal sectional view of a main part of an internal combustion engine starting rotational force transmission mechanism according to a seventh embodiment. Explanatory drawing which shows the structure of the large diameter part of the crankshaft of other embodiment. Explanatory drawing which shows the structure of the large diameter part of the crankshaft of other embodiment. Explanatory drawing which shows the structure of the large diameter part of the crankshaft of other embodiment. The perspective view which shows the structure of the outer race support plate of other embodiment. The principal part longitudinal cross-sectional view of the internal combustion engine starting rotational force transmission mechanism using the outer race support plate of FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 2 ... Cylinder block, 2a ... Arc-shaped seal fitting part, 4 ... Crankshaft, 4a ... Journal, 6 ... Flywheel (or drive plate), 8 ... Outer race support plate, 10 ... Ring gear, 10a ... Bending part, 10b ... Gear part, 12 ... Large diameter part, 12a ... Rear end face, 12b ... Outer peripheral face, 12c ... Front end face, 14 ... One-way clutch, 14a ... Sprag, 14b ... Cage, 16 ... Inner race, 16a ... Inner peripheral face, 16b ... outer peripheral surface, 18 ... ball bearing, 18a ... inner race, 18b ... outer race, 18c ... thrust bearing, 18d ... ball, 20 ... outer race, 20a ... seal sliding surface, 22 ... oil passage, 24 ... first Oil seal member, 24a ... main seal lip, 24b ... sub seal lip, 26 ... second oil seal member, 26a ... main seal lip , 26b ... secondary seal lip, 30 ... radial groove, 30a ... side face, 32 ... circumferential groove, 32a ... opening, 34 ... through hole, 34a ... opening, 104 ... crankshaft, 112 ... large diameter part, 112b ... outer peripheral surface 118a ... inner race, 132 ... circumferential groove, 134 ... through hole, 136 ... circumferential groove, 210 ... ring gear, 214 ... one-way clutch, 216 ... inner race, 218 ... ball bearing, 218a ... inner race, 218b ... outer Race, 234 ... through hole, 238, 240 ... through hole, 240 ... diameter through hole, 310 ... ring gear, 314 ... one-way clutch, 316 ... inner race, 316a ... inner peripheral surface, 316b ... circumferential groove, 318 ... Ball bearing, 318b ... outer race, 319 ... outer peripheral surface, 319a ... circumferential groove, 338, 340 ... through hole, 402 Cylinder block, 408 ... outer race support plate, 408a ... inner surface, 410 ... ring gear, 412 ... large diameter portion, 412b ... outer peripheral surface, 412c ... front end surface, 414 ... one-way clutch, 418 ... ball bearing, 418a ... inner race, 418c ... inner peripheral surface, 419 ... peripheral groove, 422 ... oil channel, 430 ... radial groove, 430a ... side surface, 432 ... peripheral groove, 432a ... opening, 432b ... opening, 512 ... large diameter portion, 512b ... outer peripheral surface, 512c ... Front end face, 530 ... Radial groove, 530a ... Side face, 532 ... Circumferential groove, 604 ... Crankshaft, 612 ... Large diameter part, 612b ... Outer face, 614 ... One-way clutch, 618 ... Ball bearing, 618a ... Inner race 630 ... Radial groove, 630a ... Side, 634 ... Through hole, 704 ... Crankshaft, 712 ... Large diameter part, 712b ... Outside Peripheral surface, 712c ... front end surface, 730a, 730b, 730c ... one set of radial grooves, 732 ... peripheral surface groove, 804 ... crankshaft, 812 ... large diameter part, 812b ... outer peripheral surface, 812c ... front end surface, 830 ... radial Ridge, 830a ... side surface, 832 ... circumferential groove, 912 ... large diameter portion, 912b ... outer peripheral surface, 912c ... front end surface, 930a, 930b ... radial ridge, 932 ... peripheral groove, 954 ... crankshaft, 958 ... Outer race support plate, 958a ... Ball bearing side surface (inner surface), 959 ... Fin, 964 ... One-way clutch, 968 ... Ball bearing, C ... Rotating shaft.

Claims (17)

A ring gear is supported on the outer peripheral surface of the large-diameter portion formed on the rotation output shaft of the internal combustion engine via a bearing, and the outer peripheral surface of the large-diameter portion is connected to the ring gear and the output shaft side member provided on the rotation output shaft of the internal combustion engine. By connecting via a one-way clutch arranged on the outer side, a rotational force in one direction by the starting motor is transmitted from the ring gear to the rotational output shaft of the internal combustion engine, and the rotational force in the reverse direction prevents transmission. A lubrication structure in an engine starting rotational force transmission mechanism,
The large-diameter portion is provided on the end face of the large-diameter portion facing the internal combustion engine main body, and contacts the lubricating oil flowing from the internal combustion engine main-body side, whereby the large-diameter portion is caused to rotate by rotating the internal combustion engine rotation output shaft. An internal combustion engine starting rotational force transmission mechanism lubrication structure comprising an outward movement promoting surface for applying a force toward the outer peripheral side of the internal combustion engine. 2. The internal combustion engine start rotation according to claim 1, wherein the one-way clutch is disposed with respect to the ring gear in a state where a portion of the ring gear supported by the bearing is sandwiched on the opposite side of the bearing. Force transmission mechanism lubrication structure. In Claim 1 or 2, the bearing is a rolling bearing,
A through hole that penetrates the inner race of the bearing in a radial direction;
A circumferential groove formed on one or both of an inner circumferential surface of the inner race of the bearing and an outer circumferential surface of the large-diameter portion, opened to at least the internal combustion engine body side, and reaching the opening of the through hole;
An internal combustion engine starting rotational force transmission mechanism lubrication structure comprising: 4. The internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 3, wherein the circumferential groove includes a circumferential groove formed in the circumferential direction and connecting all the openings of the through holes. In Claim 3 or 4, a ring-shaped seal member is arranged between the ring gear and the output shaft side member, and between the ring gear and the internal combustion engine body, respectively.
The inner edge portion of the ring gear is attached to the bearing on the inner peripheral surface side, and forms an inner race of the one-way clutch on the outer peripheral surface side and a through hole that penetrates in the radial direction. An internal combustion engine starting rotational force transmission mechanism lubrication structure characterized by forming a radial through hole communicating with a through hole of an inner race of the one-way clutch. 6. The circumferential groove according to claim 5, wherein one or both of an inner circumferential surface of the inner race of the one-way clutch and an outer circumferential surface of the outer race of the bearing are formed in the circumferential direction and communicate with all the openings of the through holes. An internal combustion engine starting rotational force transmission mechanism lubrication structure characterized by comprising: A ring gear is supported on the outer peripheral surface of the large-diameter portion formed on the rotation output shaft of the internal combustion engine via a bearing, and the outer peripheral surface of the large-diameter portion is connected to the ring gear and the output shaft side member provided on the rotation output shaft of the internal combustion engine. By connecting via a one-way clutch arranged on the outer side, a rotational force in one direction by the starting motor is transmitted from the ring gear to the rotational output shaft of the internal combustion engine, and the rotational force in the reverse direction prevents transmission. A lubrication structure in an engine starting rotational force transmission mechanism,
A peripheral surface that is formed on one or both of the inner peripheral surface of the inner race of the bearing and the outer peripheral surface of the large-diameter portion, and that opens on both the internal combustion engine body side and the opposite side of the internal combustion engine body. Groove,
The large-diameter portion is provided on the end face of the large-diameter portion facing the internal combustion engine main body, and contacts the lubricating oil flowing from the internal combustion engine main-body side, whereby the large-diameter portion is caused to rotate by rotating the internal combustion engine rotation output shaft. An outward movement promoting surface that imparts a force toward the outer peripheral side of the
An internal combustion engine starting rotational force transmission mechanism lubrication structure comprising: In any one of Claims 3-7, the said outward movement promotion surface is formed in the end surface of the said large diameter part as the side surface of the radial groove | channel or radial protrusion formed radially from the rotation center side to the outer peripheral side. An internal combustion engine starting rotational force transmission mechanism lubrication structure. In Claim 8, When the said outward movement promotion surface is formed as a side surface of the said radial groove, the outer peripheral side edge part of this radial groove has reached the opening of the said peripheral groove. Internal combustion engine starting torque transmission mechanism lubrication structure. The internal combustion engine starting rotation according to claim 8 or 9, wherein the radial groove is wider than the opening of the circumferential groove on the rotation center side and close to the opening width of the circumferential groove on the outer periphery side. Force transmission mechanism lubrication structure. In claim 8, a plurality of the radial grooves or radial ridges form a set, and the arrangement width of each set of the radial grooves or radial ridges is wider than the opening of the circumferential groove on the rotation center side. An internal combustion engine starting rotational force transmission mechanism lubrication structure characterized in that the outer circumferential side is close to the opening width of the circumferential groove. 9. The internal combustion engine start according to claim 8, wherein when the outward movement promoting surface is formed as a side surface of the radial groove, the radial groove is gradually deepened toward the opening of the circumferential groove. Rotational force transmission mechanism lubrication structure. 3. The outward movement promoting surface according to claim 1, wherein the outward movement promoting surface is formed as a side surface of a radial groove or a radial protrusion radially formed on the end surface of the large diameter portion from the rotation center side to the outer peripheral side. An internal combustion engine starting rotational force transmission mechanism lubrication structure. In Claim 13, the bearing is a rolling bearing, the inner race of the bearing is provided with a through-hole penetrating in the radial direction, the outward movement promoting surface is formed as a side surface of the radial groove, An internal combustion engine starting rotational force transmission mechanism lubricating structure characterized in that the radial grooves are gradually deepened toward the outer peripheral side of the large diameter portion to reach the through hole. 15. The output shaft side member according to claim 1, wherein the output shaft side member is provided on the internal combustion engine rotation output shaft so as to cover a side opposite to the internal combustion engine main body side with respect to the bearing, and the output shaft An internal combustion engine starting rotational force transmission mechanism lubrication structure characterized in that the bearing side surface of the side member forms a fin for pushing out lubricating oil from the rotation center side to the outer peripheral side. 16. The lubrication structure for an internal combustion engine starting rotational force transmission mechanism according to claim 15, wherein the fin surface is subjected to an oil-repellent surface treatment. 17. The internal combustion engine starting rotational force transmission mechanism lubrication structure according to claim 1, wherein an oil-repellent surface treatment is applied to at least the outward movement promoting surface of the end surface of the large-diameter portion.

Images