JP2011032961A - Starter for internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the diameter of a seal member and improve reliability of a seal function, by arranging the seal member in parallel to a torque transmission section between both the surfaces of an inner race and an outer race. <P>SOLUTION: This starter includes: a ring gear 22 rotatably connected to a starter motor 11; the outer race 26 rotated integrally with the ring gear 22; the inner race 12 positioned toward a center from the outer race 26 and rotated integrally with a crankshaft 10; the torque transmission section 27 of a one-way clutch 20 arranged between the inner race 12 and the outer race 26: and a first seal member 19 arranged in parallel to the torque transmission section 27 between both the surfaces of the inner race 12 and the outer race 26. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a starter for an internal combustion engine.

  A mechanism for transmitting the driving force of the starter motor to the crankshaft is disclosed in Patent Document 1. This is a starting device in which a ring gear, a one-way clutch, and the like are arranged between a starter motor and a crankshaft, and employs a system in which the starter motor and the ring gear are always meshed.

  In the starter described above, when the starter motor is driven, the ring gear connected to the starter motor rotates, and the rotational force is transmitted to the crankshaft via the one-way clutch to start the internal combustion engine. On the other hand, when the crankshaft rotates at a speed higher than that of the starter motor after the internal combustion engine is started, torque transmission from the crankshaft side to the ring gear side is interrupted by the one-way clutch, thereby preventing the starter motor from over-rotating.

  Here, the ring gear is bent in a crank shape so as to go around the one-way clutch, and the center side of the bent portion (the axial center side of the crankshaft and the inner peripheral side) is inserted into the end of the crankshaft via a bearing. Attached to the inner race of the one-way clutch. Further, the outer race of the one-way clutch located on the outer peripheral side of the inner race is attached to the crankshaft side. Therefore, the inner race is rotated integrally with the ring gear, and the outer race is rotated integrally with the crankshaft. An annular seal member is disposed between the outer peripheral side of the bent portion of the ring gear and the outer race, and an oil seal of the one-way clutch is made by this seal member.

JP 2007-32491 A

  By the way, in the above-mentioned conventional starting device, the seal member is forced to be arranged on the outer peripheral side away from the center of the crankshaft, and there is a hate that the diameter of the seal member becomes large. However, when the seal member is in contact with the ring gear and the outer race at a position away from the center in this way, the peripheral speed at the contact portion is large, and the seal member deteriorates due to frictional heat due to sliding, and as a result There was a risk that the sealing performance would deteriorate.

  The present invention has been completed based on the above circumstances, and an object thereof is to improve the reliability of the sealing performance.

  As means for achieving the above object, the invention of claim 1 is a starting device for starting the internal combustion engine by transmitting the driving force of the starter motor to the crankshaft, and is rotatably connected to the starter motor. A ring gear, an outer race that rotates integrally with the ring gear, an inner race that is positioned closer to the center than the outer race and rotates integrally with the crankshaft, and the inner race and the outer race. The torque transmission part of the one way clutch arrange | positioned, and the place provided with the sealing member arrange | positioned in parallel with the said torque transmission part between both surfaces of the said inner race side and the said outer race side.

  The invention of claim 2 is characterized in that, in the invention of claim 1, an oil hole for supplying oil to the seal member is formed in the inner race side surface.

  According to a third aspect of the present invention, in the first aspect of the present invention, a cylinder block is disposed on an outer peripheral side of the crankshaft, and the cylinder block communicates with an oil supply passage in the cylinder block, and the oil supply It is characterized in that a jet hole is formed for injecting oil in the road between the inner race side and the crankshaft side.

  According to a fourth aspect of the present invention, in any one of the first to third aspects, between the outer race side surface and the outer peripheral side of the crankshaft, the torque transmitting portion and the seal member are provided. It is characterized in that the bearings are arranged in parallel.

<Invention of Claim 1>
The outer race is rotated integrally with the ring gear, the inner race is rotated integrally with the crankshaft, and the seal member is arranged in parallel with the torque transmission part between the inner race side and the outer race side. As compared with the above, the diameter dimension of the seal member is reduced. Therefore, the peripheral speed at the contact portion of the seal member is also reduced, and the progress of deterioration of the seal member is suppressed, so that a predetermined sealing performance can be maintained.

<Invention of Claim 2>
In order to cool the seal member, it is required to supply oil to the seal member. However, since this seal member is disposed in parallel with the torque transmission portion between both the inner race side and the outer race side, it is difficult to secure an oil supply path to the seal member. In that respect, according to the present invention, since the oil hole is formed in the inner race side surface, the oil can be smoothly supplied to the seal member.

<Invention of Claim 3>
Oil is injected from the jet holes formed in the cylinder block between the inner race side and the crankshaft side, and the injected oil is supplied to the seal member through the oil holes. For this reason, the oil can be stably and reliably supplied to the seal member.

<Invention of Claim 4>
Since the bearing is arranged in parallel with the torque transmission portion and the seal member between the outer race side surface and the outer peripheral side of the crankshaft, the ring gear and the crankshaft can be smoothly rotated relative to each other. Also, unlike the case where a bearing is arranged between the cylinder block and the ring gear, the positional accuracy in the radial direction of the one-way clutch is excellent.

Sectional drawing of the starting device of Embodiment 1 of this invention Sectional drawing of the starting device of Embodiment 2. Sectional drawing of the starting device of Embodiment 3 Sectional drawing of the starting device of Embodiment 4. Sectional drawing of the starting device of Embodiment 5.

<Embodiment 1>
Embodiment 1 of the present invention will be described with reference to FIG. The first embodiment exemplifies a constant mesh starting device configured between the crankshaft 10 and the starter motor 11.

  An inner race 12 and a flywheel 13 are attached to the end of the crankshaft 10 by fastening them with bolts 14 that pass through both of them, whereby the inner race 12 and the flywheel 13 are rotated together with the crankshaft 10. The The inner race 12 has an annular plate shape having an opening into which the end of the crankshaft 10 can be fitted at the center thereof, and has a stepped shape along the outer peripheral surface of the crankshaft 10.

  The end of the crankshaft 10 is rotatably supported by the cylinder block 16 via a bearing metal 15. The cylinder block 16 is disposed on the outer peripheral side of the crankshaft 10 and close to the side of the inner race 12. An oil supply passage 17 is formed inside the cylinder block 16, and oil in the oil supply passage 17 is supplied to the bearing metal 15. A part of the oil is used for lubricating a bearing 18 and a one-way clutch 20 described later, and further used for cooling first and second seal members 19 and 21 described later.

  A ring gear 22 is disposed at a position away from the center (rotation center) of the crankshaft 10 toward the outer peripheral side. The ring gear 22 has an annular plate shape having a gear portion 23 on the outer periphery thereof and is bent in the middle in the radial direction so as to avoid the overhanging portion 24 of the cylinder block 16. A flywheel 13 is disposed close to the side of the ring gear.

  A pinion gear 25 is formed on the output shaft of the starter motor 11, and the gear portion 23 of the ring gear 22 is always meshed with the pinion gear 25. As a result, the driving force of the starter motor 11 is transmitted to the ring gear 22, so that the ring gear 22 is rotated about the central axis of the crankshaft 10.

  An outer race 26 is attached to the inner peripheral portion of the ring gear 22 by bolting, whereby the outer race 26 is rotated integrally with the ring gear 22. The outer race 26 is arranged on the outer peripheral side of the inner race 12 and opposite to the inner race 12, and has an annular space between the inner race 12. The outer race 26 has an annular plate shape that is thicker than the inner race 12. An annular bearing 18 is disposed between the outer circumferential surface of the outer race 26 and the inner circumferential surface of the overhanging portion 24 of the cylinder block 16, and an annular second seal member 21 is disposed in parallel with the bearing 18. Yes. The second seal member 21 is disposed at a position farther from the side surface of the cylinder block 16 than the bearing 18 and plays a role of preventing leakage of oil supplied to the bearing 18. The second seal member 21 is fixed to the projecting portion 24 of the cylinder block 16, and the second seal member 21 is slidably contacted on the outer peripheral surface of the outer race 26 with the relative rotation of the outer race 26 on the inner peripheral side. Two lips 21A are formed.

A torque transmitting portion 27 of the one-way clutch 20 is disposed in an annular space between the opposing surfaces of the outer race 26 and the inner race 12. The one-way clutch 20 is constituted by a torque transmission unit 27, an outer race 26, and an inner race 12.
The torque transmitting portion 27 is disposed in a region on the left side (side surface side of the cylinder block 16) in the figure in the annular space, and is in a positional relationship of wrapping with the bearing 18 in a direction parallel to the axial direction (axial direction of the crankshaft 10). is there. Specifically, the torque transmission unit 27 includes a sprag 27A, an outer holder 27B, an inner holder 27C, and a spring (not shown). The sprags 27A are held by the outer holder 27B and the inner holder 27C, and a plurality of sprags 27A are arranged at regular intervals in the circumferential direction. The outer cage 27B is locked to the outer race 26, and the inner cage 27C is locked to the inner race 12.

  When the internal combustion engine is started, the pinion gear 25 is rotated as the starter motor 11 is driven, the ring gear 22 is rotated, and the outer race 26 and the inner race 12 are engaged with each other via the sprag 27A. Thus, the rotational force of the ring gear 22 is transmitted to the crankshaft 10 side. On the other hand, when the rotational speed of the crankshaft 10 exceeds the rotational speed of the ring gear 22 after the internal combustion engine is started, the outer race 26 and the inner race 12 are disengaged by the tilting of the sprags 27A, and the starter starts from the crankshaft 10 side. Torque transmission to the motor 11 side is interrupted. Therefore, it is avoided that a forcible rotational force acts from the crankshaft 10 side to the starter motor 11 side, and the starter motor 11 is put into a protected state.

  An annular first seal member 19 is arranged in parallel with the torque transmitting portion 27 in the annular space between the opposing surfaces of the outer race 26 and the inner race 12. The first seal member 19 is disposed at a position farther from the side surface of the cylinder block 16 than the torque transmission portion 27 and plays a role of preventing leakage of oil supplied to the one-way clutch 20. The first seal member 19 is fixed to the inner peripheral surface (opposing surface) of the outer race 26, and the outer periphery of the inner race 12 is attached to the inner peripheral side of the first seal member 19 along with the relative rotation of the inner race 12. A first lip 19 </ b> A that slidably contacts the surface (opposing surface) is formed.

  In short, the first seal member 19 has a smaller diameter than the second seal member 21, and the inner diameter thereof is substantially equal to the outer diameter of the inner race 12, and the outer diameter thereof is substantially equal to the inner diameter of the outer race 26. In addition, the first and second seal members 19 and 21 are in a positional relationship of wrapping with each other in a direction parallel to the axial direction.

  As described above, in this embodiment, the outer race 26 is rotated integrally with the ring gear 22, the inner race 12 is rotated integrally with the crankshaft 10, and the first seal member 19 is rotated with the inner race 12 and the outer race 26. It is set as the structure arrange | positioned in parallel with the torque transmission part 27 between both opposing surfaces. Therefore, when the oil seal of the one-way clutch 20 is executed, the diameter of the first seal member 19 is smaller than that of the conventional one, so that the peripheral speed at the contact portion between the first lip 19A and the inner race 12 is reduced, and sliding It is possible to suppress an excessive increase in frictional heat associated with. As a result, the progress of deterioration of the first seal member 19 can be prevented, and as a result, the reliability of the sealing performance can be improved. Further, according to the present embodiment, the shapes of the outer race 26 and the inner race 12 can be simplified as compared with the conventional one, and the entire apparatus can be reduced in the radial direction.

<Embodiment 2>
FIG. 2 shows Embodiment 2 of the present invention. In the second embodiment, the arrangement of the bearing 18 and the oil supply structure to the first seal member 19 are different from those in the first embodiment. Others are the same as those of the first embodiment, and a duplicate description is omitted.

  That is, the bearing 18 is disposed in an annular space between the opposing surfaces of the outer race 26 and the inner race 12 so as to be parallel to and sandwiched between the torque transmission portion 27 and the first seal member 19. On both opposing surfaces of the outer race 26 and the inner race 12, a step 28 to which the outer peripheral edge portion of the bearing 18 is fitted is formed. Further, the bearing 18 is disposed so as to be able to contact the outer retainer 27B and the inner retainer 27C of the torque transmitting portion 27.

  The first seal member 19 has a size corresponding to that of the bearing 18, and has an inner diameter substantially equal to the inner diameter of the bearing 18 and an outer diameter substantially equal to the outer diameter of the bearing 18. Moreover, the torque transmission part 27 has the positional relationship which wraps with the 2nd seal member 21 about the direction parallel to an axial direction.

  An oil hole 29 having a circular cross section is formed in the inner race 12 so as to penetrate in the radial direction. The inlet of the oil hole 29 opens to the inner peripheral surface of the inner race 12, and the outlet of the oil hole 29 opens to the outer peripheral surface of the inner race 12. A groove-shaped first oil passage 30 extending in parallel with the axial direction is formed between the inner peripheral surface of the inner race 12 and the outer peripheral surface of the crankshaft 10. The inlet of the first oil passage 30 opens at a position facing the side surface of the cylinder block 16 on the side surface of the inner race 12, and the outlet of the first oil passage 30 is the inlet of the oil hole 29 on the inner peripheral surface of the inner race 12. It opens to the position where it communicates with.

  A groove-shaped second oil passage 31 extending in parallel with the axial direction is formed between the outer peripheral surface of the inner race 12 and the inner peripheral surface of the bearing 18. The inlet of the second oil passage 31 opens at a position communicating with the outlet of the oil hole 29 on the outer peripheral surface of the inner race 12, and the outlet of the second oil passage 31 opens at a position facing the first seal member 19. . Furthermore, a jet hole 32 that extends across the oil supply passage 17 is formed in the side surface of the cylinder block 16 so as to open. The jet hole 32 has a circular cross section with a smaller diameter than the oil supply passage 17. The opening of the jet hole 32 is disposed at a position facing the entrance of the first oil passage 30, that is, disposed at a position facing between the inner race 12 and the crankshaft 10.

  With such a configuration, a part of the oil flowing in the oil supply passage 17 is injected toward the entrance of the first oil passage 30 through the jet holes 32, and further from the entrance of the first oil passage 30 to the oil holes. Through the inlet of 29, it reaches the outlet of the oil hole 29, flows from there through the second oil passage 31, cools the first seal member 19, and lubricates the sliding portions of the bearing 18 and the torque transmitting portion 27. For this reason, oil is stably supplied also to the first seal member 19 located between the outer race 26 and the inner race 12, and the temperature rise of the first seal member 19 due to sliding can be suppressed. Reliability is improved.

  Further, according to the second embodiment, since the bearing 18 is disposed between the outer race 26 and the inner race 12, the relative rotation of the ring gear 22 and the crankshaft 10 is performed smoothly. Further, since the bearing 18 is not disposed between the cylinder block 16 and the ring gear 22, it is easy to obtain the positional accuracy in the radial direction of the one-way clutch 20.

<Embodiment 3>
FIG. 3 shows Embodiment 3 of the present invention. In the third embodiment, the arrangement of the bearings 18 and the shape of the inner race 12 are different from those in the second embodiment.
That is, the inner race 12 has an annular shape fitted to the outer peripheral surface of the end portion of the crankshaft 10, and unlike the second embodiment, it does not have a stepped portion at the left end portion as shown in the drawing. On the other hand, the left end portion of the inner race surface of the outer race 26 in the drawing is a shaft facing surface 26 </ b> A that faces the outer circumferential surface of the crankshaft 10. Between the inner circumferential surface of the outer race 26 excluding the shaft facing surface 26A and the inner circumferential surface of the inner race 12, the torque transmission portion 27 and the first seal member 19 are sequentially arranged from the side closer to the side surface of the cylinder block 16. Is arranged.

  A step portion 33 is formed on the outer peripheral surface of the crankshaft 10 in parallel with the inner race 12, and the bolt 14 passes through the step portion 33 and the inner race 12 in a direction parallel to the axial direction. The bearing 18 is disposed between the outer peripheral surface of the step portion 33 and the shaft facing surface 26 </ b> A of the outer race 26. Therefore, the bearing 18 is disposed opposite to the side surface of the cylinder block 16. The outer peripheral surface of the stepped portion 33 is disposed so as to fall one step toward the center side from the outer peripheral surface of the inner race 12 so as to correspond to the size of the bearing 18. Other configurations are substantially the same as those of the second embodiment.

  According to the third embodiment, since the stepped portion is not formed in the inner race 12, the shape of the inner race 12 can be simplified.

<Embodiment 4>
FIG. 4 shows Embodiment 4 of the present invention. In the fourth embodiment, the shape of the inner race 12 is different from that of the second embodiment.
That is, the inner race 12 is formed integrally with the crankshaft 10. In short, the outer peripheral surface of the crankshaft 10 constitutes the inner race 12. Between the inner race 12 (the outer peripheral surface of the crankshaft 10) and the opposing surface of the outer race 26, the torque transmitting portion 27, the bearing 18, and the first seal member 19 are sequentially arranged from the side closer to the side surface of the cylinder block 16. Has been placed. The inner race 12 is formed with a groove-like oil passage 34 that extends in a direction parallel to the axial direction and faces the torque transmission portion 27, the bearing 18, and the first seal member 19, and opens to the side surface. Yes. Other configurations are substantially the same as those of the second embodiment.

  According to the fourth embodiment, since the inner race 12 that is separate from the crankshaft 10 is omitted, the configuration of the entire apparatus can be simplified and the number of parts can be reduced.

<Embodiment 5>
FIG. 5 shows Embodiment 5 of the present invention. In the fifth embodiment, the structure of the bearing 18A is different from that of the second embodiment.
That is, the bearing 18A is configured as a needle bearing in which a needle-like rolling element is incorporated. Other configurations are substantially the same as those of the second embodiment.

  According to the fifth embodiment, since the cross-sectional height of the bearing 18A is kept low, the distance between the opposing surfaces of the outer race 26 and the inner race 12 can be reduced, and as a result, the entire device can be reduced in the radial direction.

<Other embodiments>
The present invention is not limited to the embodiments described with reference to the above description and drawings. For example, the following embodiments are also included in the technical scope of the present invention.
(1) The ring gear may be formed integrally with the outer race.
(2) The torque transmission part of the one-way clutch may be a roller type instead of a sprag type.
(3) The oil holes and jet holes in the second embodiment may be applied to the configuration of the first embodiment.
(4) The needle bearing in the fifth embodiment may be applied to the configuration of the first embodiment.

DESCRIPTION OF SYMBOLS 10 ... Crankshaft 11 ... Starter motor 12 ... Inner race 17 ... Oil supply path 18, 18A ... Bearing 19 ... 1st seal member (seal member)
DESCRIPTION OF SYMBOLS 20 ... One-way clutch 22 ... Ring gear 26 ... Outer race 27 ... Torque transmission part 29 ... Oil hole 32 ... Jet hole

Claims (4)

A starting device that transmits a driving force of a starter motor to a crankshaft to start an internal combustion engine,
A ring gear rotatably connected to the starter motor;
An outer race rotated integrally with the ring gear;
An inner race that is positioned closer to the center than the outer race and is rotated integrally with the crankshaft;
A torque transmission portion of a one-way clutch disposed between the inner race and the outer race;
A starting device for an internal combustion engine, comprising: a seal member disposed between both surfaces of the inner race side and the outer race side and in parallel with the torque transmission unit.   The starter for an internal combustion engine according to claim 1, wherein an oil hole for supplying oil to the seal member is formed in the inner race side surface.   A cylinder block is disposed on the outer peripheral side of the crankshaft. The cylinder block communicates with an oil supply passage in the cylinder block, and oil in the oil supply passage is provided between the inner race side and the crankshaft side. 3. A starter for an internal combustion engine according to claim 2, wherein a jet hole for injecting toward the gap is formed.   The bearing is arrange | positioned in parallel with the said torque transmission part and the said seal member between the said outer race side surface and the outer peripheral side of the said crankshaft. A starter for an internal combustion engine as described.

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