JP2011117327A - Starting torque transmission mechanism of internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a starting torque transmission mechanism of an internal combustion engine, that can reduce noise. <P>SOLUTION: The starting torque transmission mechanism of the internal combustion engine includes an inner race 4 for being integrally rotated with a crank shaft, an outer race 6 for being integrally rotated with a ring gear that is caused to rotate in one direction by a starter motor, and a one-way clutch 10. The one-way clutch 10 has a plurality of sprags 16 provided in the circumferential direction between an outer circumference of the inner race 4 and an inner circumference of the outer race 6, and an inner cage 12 for restricting a relative movement of the sprags 16 in the circumferential direction. The one-way clutch 10 permits transmission of torque in the direction from the outer race 6 to the inner race 4, while inhibiting transmission of the torque from the inner race 4 to the outer race 6. The inner cage 12 is fixed to the inner race 4. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to an inner race that rotates integrally with a rotation output shaft of an internal combustion engine, an outer race that rotates integrally with a ring gear that is rotated in one direction by a starting motor, and an outer peripheral surface of these inner races and an inner periphery of the outer race. The present invention relates to a starting rotational force transmission mechanism for an internal combustion engine including a one-way clutch provided between the two and a surface.

  Conventionally, as a starting torque transmission mechanism of this type of internal combustion engine, for example, there is one described in Patent Document 1. There is also a starting torque transmission mechanism for an internal combustion engine having the structure shown in FIGS. FIG. 6 partially shows a cross-sectional structure along the axial direction of the crankshaft 2 in the conventional starting torque transmission mechanism. FIG. 7 shows a DD cross-sectional structure of FIG.

  As shown in FIG. 6, an inner race 104 is connected to one end of the crankshaft 2. An outer race 6 is provided on the outer periphery of the inner race 104, and a ring gear 8 to which a rotational force in one direction from the starting motor is transmitted is connected to the outer race 6. Between the outer peripheral surface of the inner race 104 and the inner peripheral surface of the outer race 6, the one-way clutch 110 and the outer race 6 are rotatably supported in order from the internal combustion engine body EB side along the axial direction of the crankshaft 2. A ball bearing 20 and a seal member 30 for preventing leakage of oil to the outside are provided. The one-way clutch 110 allows a unidirectional rotational force from the starting motor to be transmitted from the outer race 6 to the inner race 104, while preventing transmission of the rotational force from the inner race 104 to the outer race 6. To do.

  As shown in FIGS. 6 and 7, the one-way clutch 110 includes an inner cage 112, an outer cage 114, a plurality of sprags 116, and a spring 118. A plurality of sprags 116 are provided in the circumferential direction of the inner race 104 between the outer peripheral surface of the inner race 104 and the inner peripheral surface of the outer race 6. The inner cage 112 and the outer cage 114 arrange the sprags 116 apart from each other in the circumferential direction and restrict relative movement of the sprags 116 in the circumferential direction. The inner cage 112 is provided on the inner race 104 side with respect to the outer cage 114. Further, both the inner cage 112 and the outer cage 114 are provided so as to be rotatable relative to the inner race 104 and the outer race 6. The spring 118 is provided between the inner cage 112 and the outer cage 114 and urges each sprag 116 in a direction in which each sprag 116 is engaged between the inner race 104 and the outer race 6.

  In the starting rotational force transmission mechanism of the internal combustion engine having such a configuration, when the starting motor is driven at the time of starting the internal combustion engine, each sprag 116 rises and each sprag 116 bites between the inner race 104 and the outer race 6. By being in the engaged state, the one-way clutch 110 is engaged, and the rotational force of the starting motor is transmitted to the crankshaft 2 via the one-way clutch 110. After that, when the internal combustion engine is in a complete explosion state, in other words, when it is in a state where it can operate independently without borrowing the power of the starting motor, each sprag 116 falls down and the state where each sprag 116 is bitten is eliminated. Thus, the engaged state of the one-way clutch 110 is released, and transmission of the rotational force from the crankshaft 2 to the starting motor is prevented.

Japanese Patent Laid-Open No. 2001-213180

  By the way, in such a starting torque transmission mechanism, when the processing accuracy at the time of manufacture is low, a convex portion may be formed on the outer peripheral surface of the inner race 104. Therefore, after the start of the internal combustion engine is completed, the state in which each sprag 116 is caught between the inner race 104 and the outer race 6 is eliminated, and when each sprag 116 rotates relative to the inner race 104, Accordingly, the sprag 116 slides on the outer peripheral surface of the inner race 104. For this reason, there arises a problem that noise is generated by intermittent contact between the protrusions present on the outer peripheral surface of the inner race 104 and the sprags 116.

  The present invention has been made in view of such circumstances, and an object thereof is to provide a starting torque transmission mechanism for an internal combustion engine that can reduce noise.

Hereinafter, means for solving the above-described problems and the effects thereof will be described.
(1) The invention according to claim 1 is an inner race that rotates integrally with a rotation output shaft of an internal combustion engine, an outer race that rotates integrally with a ring gear that is rotated in one direction by a starting motor, and the inner race. A one-way clutch having a plurality of engagement members provided in the circumferential direction between the outer circumferential surface of the outer race and the inner circumferential surface of the outer race, and a regulating member that regulates relative movement of the engagement members in the circumferential direction. A one-way clutch that allows the rotational force in the one direction to be transmitted from the outer race to the inner race, while preventing transmission of the rotational force from the inner race to the outer race. In the engine starting torque transmission mechanism, it is necessary that the restricting member is fixed to the inner race. It is set to.

  According to this configuration, since the engaging member rotates together with the inner race together with the regulating member, the regulating member is not fixed to the inner race, that is, the engaging member rotates together with the inner race together with the regulating member. Unlike the configuration that does not, the engaging member does not rotate relative to the outer peripheral surface of the inner race. As a result, the sprag does not slide on the outer peripheral surface of the inner race after the state where the engaging member is engaged between the inner race and the outer race is eliminated. Even in the case where there is, intermittent contact between such convex portions and sprags will not occur. Therefore, noise can be reduced.

  (2) The invention according to claim 2 is the starting torque transmission mechanism of the internal combustion engine according to claim 1, wherein the inner race has a fitting groove formed on an outer peripheral surface thereof, and the regulating member is The gist is to be fitted in the fitting groove.

  According to this configuration, the restriction member can be fixed to the inner race in a simple manner by fitting the restriction member into the fitting groove formed on the outer peripheral surface of the inner race.

(3) The gist of the invention described in claim 3 is that, in the starting torque transmission mechanism of the internal combustion engine according to claim 2, the restriction member is press-fitted into the fitting groove.
According to this configuration, the regulating member can be easily and accurately fixed to the inner race by press-fitting the regulating member into the fitting groove formed on the outer peripheral surface of the inner race.

  (4) According to the invention described in any one of claims 1 to 3, according to the invention described in claim 4, between the outer peripheral surface of the inner race and the inner peripheral surface of the outer race. Can be embodied in such a manner that the one-way clutch, a rolling bearing, and a seal member are provided along the axial direction of the rotation output shaft of the internal combustion engine.

  (5) The invention according to claim 5 is the starting rotational force transmission mechanism for an internal combustion engine according to any one of claims 1 to 4, wherein the inner race is separate from the rotational output shaft of the internal combustion engine. Its gist is that it is formed by the body.

  According to this configuration, for example, in the configuration in which the invention according to claim 2 or 3 is applied to the present invention, the inner race is fitted to the inner race independent of the rotation output shaft of the internal combustion engine. Since the grooves need only be formed, such a forming process can be simplified.

  (6) The invention according to claim 6 is the starting rotational force transmission mechanism of the internal combustion engine according to any one of claims 1 to 4, wherein the outer peripheral surface of the rotation output shaft of the internal combustion engine is the inner race. The gist is to be the outer peripheral surface.

  According to this configuration, the number of components of the starting rotational force transmission mechanism of the internal combustion engine is reduced compared to a configuration in which the inner race is formed separately from the rotation output shaft of the internal combustion engine. Therefore, the configuration of the starting rotational force transmission mechanism can be simplified.

1 is a cross-sectional view partially showing a cross-sectional structure along an axial direction of a crankshaft in a starting torque transmission mechanism for an internal combustion engine according to an embodiment of the present invention. The expanded sectional view which expands and shows sectional drawing of FIG. Sectional drawing which shows the AA cross-section of FIG. The side view which shows the side structure of the inner cage in the embodiment. (A) Sectional drawing which shows BB sectional structure of FIG. 4, (b) Sectional drawing which shows CC sectional structure of FIG. Sectional drawing which shows partially the cross-sectional structure along the axial direction of a crankshaft about the conventional starting rotational force transmission mechanism. Sectional drawing which shows DD sectional structure of FIG.

Hereinafter, an embodiment in which a starting rotational force transmission mechanism for an internal combustion engine according to the present invention is embodied as a starting rotational force transmission mechanism for an in-vehicle internal combustion engine will be described with reference to FIGS.
FIG. 1 shows a cross-sectional structure of the starting rotational force transmission mechanism of the present embodiment. 1 is a partial cross-sectional view along the axial direction of the crankshaft 2 that is the rotation output shaft of the internal combustion engine, and is a partial cross-sectional view showing a portion vertically above the central axis of the crankshaft 2. is there. In the figure, the left side is the internal combustion engine body EB side, and the right side is the transmission TM side.

  As shown in the figure, the crankshaft 2 is located on the transmission TM side with respect to the large outer diameter portion 2a located outside the cylinder block 70 and the large outer diameter portion 2a, and more than the large outer diameter portion 2a. A small outer diameter portion 2b having a small outer diameter is provided. A substantially cylindrical inner race 4 is provided on the outer periphery of the large outer diameter portion 2a and the small outer diameter portion 2b. The inner race 4 has a large inner diameter portion 4 a that faces the large outer diameter portion 2 a of the crankshaft 2 and a small inner diameter portion 4 b that faces the small outer diameter portion 2 b of the crankshaft 2. The crankshaft 2 and the inner race 4 are in contact with the end face on the transmission TM side of the large outer diameter portion 2 a of the crankshaft 2 and the end face on the internal combustion engine body EB side of the small inner diameter portion 4 b of the inner race 4. Are connected via a bolt 51. A flywheel 90 is further connected to the crankshaft 2 and the inner race 4 via bolts 51.

  An outer race 6 having a substantially cylindrical shape is provided on the outer periphery of the inner race 4. The outer race 6 includes an outer race main body 6a and an annular protrusion 6b that protrudes radially outward from the outer race main body 6a. A ring gear 8 having a substantially disc shape is provided on the outer periphery of the outer race 6. The protrusion 6 b of the outer race 6 and the ring gear 8 are connected via a bolt 52. Further, a pinion gear (not shown) provided on the output shaft of the starter motor ST is meshed with the gear portion 8a of the ring gear 8, whereby one-way rotational force from the starter motor ST is transmitted to the ring gear 8. It has come to be.

  Between the outer peripheral surface of the inner race 4 and the inner peripheral surface of the outer race 6, the one-way clutch 10 and the outer race are arranged in order from the internal combustion engine body EB side to the transmission TM side along the axial direction of the crankshaft 2. A ball bearing 20 that rotatably supports 6 and an inner seal member 30 that prevents leakage of oil to the outside are provided. The one-way clutch 10 allows a unidirectional rotational force from the starter motor ST to be transmitted from the outer race 6 to the inner race 4, while the rotational force is transmitted from the inner race 4 to the outer race 6. Stop.

  A substantially annular projecting portion 70 a that projects toward the projecting portion 6 b of the outer race 6 is formed on the end face of the cylinder block 70 on the transmission TM side. A substantially annular outer seal member 80 is provided between the inner peripheral surface of the projecting portion 70a and the outer peripheral surface of the outer race main body 6a.

Next, a configuration between the outer peripheral surface of the inner race 4 and the inner peripheral surface of the outer race 6 will be described in detail with reference to FIG.
FIG. 2 is an enlarged cross-sectional view of the cross-sectional view of FIG. 1, particularly an enlarged cross-sectional view centering on the configuration between the outer peripheral surface of the inner race 4 and the inner peripheral surface of the outer race 6.

  As shown in FIG. 2, the outer diameter of the inner race 4 is reduced stepwise in the order of a portion corresponding to the one-way clutch 10, a portion corresponding to the ball bearing 20, and a portion corresponding to the inner seal member 30. Further, the inner diameter of the outer race 6 is increased stepwise in the order of a portion corresponding to the one-way clutch 10, a portion corresponding to the ball bearing 20, and a portion corresponding to the inner seal member 30.

  The ball bearing 20 includes an inner race portion 21 that is press-fitted into the outer peripheral surface of the inner race 4 in a substantially annular shape, an outer race portion 22 that is inserted into the inner peripheral surface of the outer race 6 in a substantially annular shape, A ball 23 as a rolling element provided between the inner race portion 21 and the outer race portion 22 and a snap ring 24 for fixing the outer race portion 22 to the outer race 6 are provided. In addition, the ball | bowl 23 is provided so that rolling is possible via the holder | retainer which is not illustrated.

  The inner seal member 30 has a substantially annular shape as a whole and a substantially U-shaped cross-section, and is fixed to the outer race 6. The portion of the seal member main body 31 that faces the outer peripheral surface of the inner race 4. A seal lip portion 32 having a shape projecting toward the outer peripheral surface from the entire circumference is provided. The seal lip 32 is slidably in contact with the outer peripheral surface of the inner race 4. As a result, the inner seal member 30 is located between the outer peripheral surface of the inner race 4 and the inner peripheral surface of the outer race 6 with respect to the one-way clutch 10 and the ball bearing 20 in the axial direction of the crankshaft 2. Sealing is performed at a close position to prevent oil leakage from between the outer peripheral surface of the inner race 4 and the inner peripheral surface of the outer race 6. The ball bearing 20 corresponds to the rolling bearing according to the present invention, and the inner seal member 30 corresponds to the seal member according to the present invention.

Next, the one-way clutch 10 and the inner race 4 in the present embodiment will be described in detail with reference to FIGS.
FIG. 3 shows the AA cross-sectional structure of FIG. FIG. 4 shows a side structure of the inner cage 12 of the present embodiment. FIG. 5A shows a BB cross-sectional structure of FIG. FIG. 5B shows a CC cross-sectional structure of FIG.

  As shown in FIGS. 2 and 3, the one-way clutch 10 in this embodiment is also similar to the conventional one-way clutch 110 shown in FIGS. 6 and 7, and includes an inner cage 12, an outer cage 14, and a plurality of sprags. 16 and a spring 18.

A plurality of sprags 16 are provided in the circumferential direction of the inner race 4 between the outer peripheral surface of the inner race 4 and the inner peripheral surface of the outer race 6.
Both the inner cage 12 and the outer cage 14 have an annular shape, and the inner cage 12 has a smaller inner diameter and outer diameter than the outer cage 14. The inner cage 12 is provided on the inner race 4 side with respect to the outer cage 14.

  The spring 18 is provided between the inner cage 12 and the outer cage 14 and biases each sprag 16 in a direction in which each sprag 16 is engaged between the inner race 4 and the outer race 6.

  As shown in FIGS. 4 and 5A and 5B, the inner cage 12 includes an annular cage body 12a and a bent portion 12b that is bent radially inward from one end of the cage body 12a. And have. The bent portion 12 b is provided over the entire circumference of the inner cage 12. The cage body 12a is formed with accommodation holes 12c at regular intervals for accommodating the sprags 16 and restricting the relative movement of the sprags 16 in the circumferential direction. Further, a slit 12d extending in the axial direction of the inner cage 12 is formed between the accommodation holes 12c adjacent to each other in the cage body 12a and the bent portion 12b.

  As shown in FIG. 2, a fitting groove 41 is formed over the entire circumference in a portion corresponding to the one-way clutch 10 on the outer circumferential surface of the inner race 4. Further, the inner cage 12 is fixed to the inner race 4 by the bent portion 12 b of the inner cage 12 being fitted into the fitting groove 41. In the present embodiment, the bent portion 12 b of the inner cage 12 is press-fitted into the fitting groove 41. Accordingly, the inner cage 12 rotates together with the inner race 4.

  The outer cage 14 basically has the same structure as the inner cage 12. However, the outer cage 14 is provided so as to come into contact with the inner peripheral surface of the outer race 6, and is rotatable relative to the inner race 4 and the outer race 6.

  In the starting rotational force transmission mechanism of the internal combustion engine having such a configuration, when the starting motor ST is driven at the time of starting the internal combustion engine, each sprag 16 rises and each sprag 16 is interposed between the inner race 4 and the outer race 6. By being engaged, the one-way clutch 10 is engaged, and the rotational force of the starter motor ST is transmitted to the crankshaft 2 via the one-way clutch 10. Thereafter, when the internal combustion engine is in a complete explosion state, in other words, when it is in a state where it can operate independently without borrowing the power of the starter motor ST, each sprag 16 falls down and the state in which each sprag 16 is bitten is eliminated. Thus, the engaged state of the one-way clutch 10 is released, and transmission of the rotational force from the crankshaft 2 to the starting motor ST is prevented.

In addition, the sprag 16 in this embodiment corresponds to the engaging member according to the present invention, and the inner cage 12 in the present embodiment corresponds to the regulating member according to the present invention.
According to the starting rotational force transmission mechanism of the internal combustion engine according to the present embodiment described above, the following operational effects can be obtained.

  (1) The starting torque transmission mechanism of the internal combustion engine includes an inner race 4 that rotates integrally with the crankshaft 2, and an outer race 6 that rotates integrally with a ring gear 8 that is rotated in one direction by the starting motor ST. It was supposed to be. A one-way having a plurality of sprags 16 provided in the circumferential direction between the outer peripheral surface of the inner race 4 and the inner peripheral surface of the outer race 6, and an inner cage 12 for restricting relative movement of the sprags 16 in the circumferential direction. The clutch 10 is a one-way clutch that allows the rotational force in one direction to be transmitted from the outer race 6 to the inner race 4 while preventing transmission of the rotational force from the inner race 4 to the outer race 6. 10 shall be provided. Further, the inner cage 12 is fixed to the inner race 4. As a result, the sprag 16 rotates together with the inner race 4 together with the inner cage 12, so that the inner cage is not fixed to the inner race, that is, the sprag does not rotate integrally with the inner race together with the inner cage. The sprags 16 will not rotate relative to the outer peripheral surface of the inner race 4. As a result, the sprag 16 does not slide on the outer peripheral surface of the inner race 4 after the state where the sprag 16 is engaged between the inner race 4 and the outer race 6 is eliminated. Even if there are convex portions on the surface, intermittent contact between the convex portions and the sprags 16 does not occur. Therefore, noise can be reduced.

  (2) The inner race 4 has a fitting groove 41 formed on the outer peripheral surface thereof. The inner cage 12 is fitted into the fitting groove 41. Thereby, the inner cage 12 can be fixed to the inner race 4 in a simple manner by fitting the inner cage 12 to the fitting groove 41 formed on the outer peripheral surface of the inner race 4. Become.

  (3) The inner cage 12 is press-fitted into the fitting groove 41. Accordingly, the inner cage 12 can be fixed to the inner race 4 simply and accurately by press-fitting the inner cage 12 into the fitting groove 41 formed on the outer peripheral surface of the inner race 4.

  (4) The inner race 4 is formed separately from the crankshaft 2. As a result, it is only necessary to form the fitting groove 41 in the inner race 4 in a state independent of the crankshaft 2, so that such a forming process can be simplified.

  The starting rotational force transmission mechanism for an internal combustion engine according to the present invention is not limited to the configuration exemplified in the above embodiment, and can be implemented as the following form, for example, which is appropriately modified.

  In the above embodiment, the inner race 4 is formed separately from the crankshaft 2, but instead, the outer peripheral surface of the crankshaft may be the outer peripheral surface of the inner race. In this case, compared to a configuration in which the inner race is formed separately from the crankshaft, the number of components of the starting rotational force transmission mechanism of the internal combustion engine is reduced, and thus the configuration of the mechanism may be simplified. it can.

  In the above embodiment, the one-way clutch 10, the ball bearing 20, and the inner seal member 30 are provided along the axial direction of the crankshaft 2 between the outer peripheral surface of the inner race 4 and the inner peripheral surface of the outer race 6. However, the configuration of the starting torque transmission mechanism according to the present invention is not limited to this. Instead of such a configuration, for example, an inner seal member may not be provided between the outer peripheral surface of the inner race and the inner peripheral surface of the outer race. In short, it is sufficient if at least a one-way clutch is provided between the outer peripheral surface of the inner race and the inner peripheral surface of the outer race.

  The mode of fitting and fixing the inner cage 12 in the fitting groove 41 is not limited to the press-fitting exemplified in the above embodiment. In addition, for example, the inner cage may be inserted into the fitting groove, and a fixing piece for fixing the inner cage 12 to the inner race may be separately attached.

  The configuration of the regulating member is not limited to the inner cage 12 illustrated in the above embodiment, and the configuration is arbitrarily changed as long as the relative movement in the circumferential direction of the plurality of sprags 16 is regulated. Can do.

  In the above embodiment, the restriction member is fitted and fixed to the fitting groove formed on the outer peripheral surface of the inner race, but the present invention is not limited to this, and the restriction member is If fixed to the inner race, the fixing mode can be arbitrarily changed.

  2 ... crankshaft, 2a ... large outer diameter part, 2b ... small outer diameter part, 4, 104 ... inner race, 4a ... large inner diameter part, 4b ... small inner diameter part, 6 ... outer race, 6a ... outer race body, 6b ... Projection part, 8 ... Ring gear, 8a ... Gear part, 10, 110 ... One-way clutch, 12, 112 ... Inner cage, 12a ... Cage body, 12b ... Bent part, 12c ... Housing hole, 12d ... Slit, 14, 114 ... Outer cage, 16, 116 ... Sprag, 18, 118 ... Spring, 20 ... Ball bearing, 21 ... Inner race portion, 22 ... Outer race portion, 23 ... Ball, 24 ... Snap ring, 30 ... Inner seal member, 31 ... Seal Member body 32 ... Seal lip part 41 ... Fitting groove 51, 52 ... Bolt 70 ... Cylinder block 70a ... Projection part, 0 ... outer seal member, 90 ... flywheel, ST ... starting motor, EB ... engine body, TM ... transmission.

Claims (6)

An inner race that rotates integrally with the rotation output shaft of the internal combustion engine;
An outer race that rotates integrally with a ring gear that is rotated in one direction by a starting motor;
A one-way clutch having a plurality of engagement members provided in the circumferential direction between the outer circumferential surface of the inner race and the inner circumferential surface of the outer race, and a regulating member that regulates relative movement of the engagement members in the circumferential direction. A one-way clutch that allows the rotational force in the one direction to be transmitted from the outer race to the inner race, while preventing transmission of the rotational force from the inner race to the outer race; In a starting torque transmission mechanism of an internal combustion engine comprising:
The starting rotational force transmission mechanism for an internal combustion engine, wherein the restricting member is fixed to the inner race. The starting rotational force transmission mechanism for an internal combustion engine according to claim 1,
The inner race has a fitting groove formed on the outer peripheral surface thereof,
The starting rotational force transmission mechanism for an internal combustion engine, wherein the regulating member is fitted in the fitting groove. The starting rotational force transmission mechanism for an internal combustion engine according to claim 2,
The starting rotational force transmission mechanism for an internal combustion engine, wherein the regulating member is press-fitted into the fitting groove. In the starting rotational force transmission mechanism of the internal combustion engine according to any one of claims 1 to 3,
Between the outer peripheral surface of the inner race and the inner peripheral surface of the outer race, the one-way clutch, a rolling bearing, and a seal member are provided along the axial direction of the rotation output shaft of the internal combustion engine. A starting rotational force transmission mechanism for an internal combustion engine. In the starting rotational force transmission mechanism of the internal combustion engine according to any one of claims 1 to 4,
The inner race is formed separately from the rotation output shaft of the internal combustion engine. In the starting rotational force transmission mechanism of the internal combustion engine according to any one of claims 1 to 4,
A starting rotational force transmission mechanism for an internal combustion engine, wherein an outer peripheral surface of a rotation output shaft of the internal combustion engine is an outer peripheral surface of the inner race.

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