JP2009068580A - Torque transmitting device for starting engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a torque transmitting device for starting an engine, capable of setting a separative rotating speed of a clutch 6 lower. <P>SOLUTION: A roller type clutch 6 used for this torque transmitting device has a retainer 17 (an inertial body) moving by interlocking with the movement of its roller 15 when the roller 15 moves in the peripheral direction in a cam chamber 14. In this clutch 6, an engine is ignited, and in a moment when a rotating speed of an outer 13 becomes an overrun state of exceeding a rotating speed of an inner 12, the roller 15 and the retainer 17 tries to rest on the spot by inertial mass possessed by both. That is, in a moment when the outer 13 starts to rotate at a high speed, inertial force likely to move in the anti-wedge direction of the cam chamber 14 against a load of a spring 16, operates on the roller 15 and the retainer 17. As a result, the roller 15 can be centrifuged from an outer peripheral surface of the inner 12 at a rotating speed lower than a conventional roller type clutch having no retainer 17. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an engine starting torque transmission device for transmitting a driving torque of a starter to an engine crankshaft to start the engine.

In recent years, an idling stop system that automatically stops an engine when a signal stops at an intersection, for example, has been put into practical use as an exhaust gas countermeasure for automobiles, which is one of the causes of global warming. As a prior art applied to the system, there is a torque transmission device described in Patent Document 1.
This torque transmission device has a ring gear with a built-in one-way clutch, and this ring gear is assembled to a flywheel attached to an engine crankshaft through a bearing so as to be relatively rotatable, and is always mounted on a starter pinion gear. It is engaged.

The clutch built in the ring gear is composed of an inner provided integrally with the ring gear, an outer connected to the flywheel, and an engagement member for intermittently transmitting torque between the inner and the outer. Is started, that is, when the drive torque of the starter is transmitted from the pinion gear to the ring gear, the engagement element is locked between the inner and the outer, and the rotation of the ring gear is transmitted to the flywheel side.
On the other hand, when the flywheel is driven and rotated by the engine by the start of the engine, that is, when the rotational speed of the flywheel exceeds the rotational speed of the ring gear, the engaging element is centrifuged from the outer peripheral surface of the inner, As the clutch idles, torque transmission from the flywheel side to the ring gear side is interrupted.
JP 2000-274337 A

  The one-way clutch used in the above torque transmission device is connected to the flywheel on the engine side while the rotation of the inner provided on the internal gear is stopped when the starter is stopped after the ignition of the engine. The outer is always rotating. That is, since the clutch is always idling while the engine is rotating, it is necessary to centrifugally separate the engagement element from the outer peripheral surface of the inner. Generally, a sprag clutch or a cam clutch having a cam effect is used. ing.

  On the other hand, a roller clutch in which a cam chamber is formed on the inner periphery of the outer and a roller is arranged in the cam chamber has a roller that rotates when the clutch is idle as compared with the sprag clutch or cam clutch described above. Excellent wear resistance. However, since this roller clutch has a spring load that presses the roller into the narrow space of the cam chamber, the roller is separated in an overrun state after engine ignition when torque is transmitted (especially when the engine is misfired). The rotation speed (referred to as the separation rotation speed) to be increased. For this reason, it is difficult to set the clutch separation rotational speed to be equal to or lower than, for example, the idle rotational speed, and it is difficult to employ a roller clutch in the above-described torque transmission device.

  The present invention has been made based on the above circumstances, and an object of the present invention is to start an engine that can set the clutch separation rotational speed lower in a configuration in which a one-way clutch is built in a ring gear that is a first rotating body. The object is to provide a torque transmission device.

(Invention of Claim 1)
The present invention is an engine starting torque transmission device for transmitting a driving torque generated by a starter to an engine crankshaft to start the engine, and includes a first rotation having a gear portion that always meshes with a pinion gear of the starter. A first rotating body, a second rotating body that is fixed to the crankshaft and rotates integrally with the crankshaft, and the first rotating body and the second rotating body. When the first rotating body is driven by the starter to rotate, torque is transmitted from the first rotating body to the second rotating body, and the second rotating body is driven by the engine. A one-way clutch that shuts off torque transmission from the second rotating body to the first rotating body when rotating, the clutch having an inner having a circular outer peripheral surface on the first rotating body; The second rotating body has an inner An outer that forms a wedge-shaped cam chamber with the outer peripheral surface, a roller disposed in the cam chamber, a spring that directly or indirectly presses the roller toward the narrow direction of the cam chamber, and an outer And an inertial body that moves in the same direction as the roller in conjunction with the movement of the roller when the roller moves in the circumferential direction by relative rotation with the inner.

  In the clutch of the present invention, since the outer is provided on the second rotating body fixed to the crankshaft of the engine, when the engine is ignited and the acceleration of the engine is increased, the rotation of the outer is rapidly increased, The outer rotational speed exceeds the inner rotational speed, that is, an overrun state occurs. Here, in the conventional roller type clutch having no inertia body, since the inertia mass of the roller is small, the roller easily follows the rotation of the outer at the moment when the engine is ignited and the outer starts to rotate at high speed. Try to move in the direction of rotation). Thereafter, as the rotation of the outer increases, the cam chamber gradually moves in a direction (referred to as an anti-wedge direction), so that the rotational speed when the roller is centrifuged from the outer peripheral surface of the inner inevitably increases. Get higher.

  On the other hand, the clutch of the present invention, at the moment when it shifts to the overrun state, even if the outer starts to rotate at a high speed, the roller and the inertial body try to stand still on the spot due to the inertial mass of both. When compared with a roller clutch, it becomes difficult to follow the rotation of the outer. In other words, the apparent force (inertia force) that tries to move the cam chamber in the anti-wedge direction acts on the roller and the inertia body at the moment when the outer starts to rotate at high speed. Thereby, it is possible to centrifuge the roller from the outer peripheral surface of the inner at a lower rotational speed (for example, lower than the idling speed) as compared with a conventional roller clutch without an inertial body.

  Further, when the engine is restarted immediately after the misfire, a negative acceleration is generated in the engine. That is, the outer rotation is decelerated rapidly. In this case, contrary to when the engine is ignited, an inertial force is applied to the roller and the inertial body so as to move in the wedge direction of the cam chamber. That is, since the inertial force acts in the direction in which the spring biases the roller, the roller can move faster in the wedge direction of the cam chamber. As a result, the clutch can be quickly engaged and the engine can be restarted in a short time.

(Invention of Claim 2)
In the engine start torque transmitting device according to claim 1, the inertial body is in sliding contact with the outer peripheral surface of the inner directly, or an indirect part is disposed between the inertial body and the inner, and the indirect part is interposed therebetween. It is characterized by being in sliding contact with the outer peripheral surface of the inner indirectly.
In the clutch according to the present invention, when the inner and the inertial body rotate relative to each other, the inertial body directly or indirectly slides on the outer peripheral surface of the inner to generate a sliding resistance. This sliding resistance makes it difficult for the roller and the inertial body to follow the rotation of the outer when the outer starts to rotate at a high speed due to the ignition of the engine. Therefore, in cooperation with the inertial force described in the invention of claim 1, It is possible to further reduce the clutch separation rotational speed, and to increase the degree of design freedom.

(Invention of Claim 3)
3. The engine start torque transmitting device according to claim 1 or 2, wherein the inertial body includes an outer peripheral surface of the inner when the outer rotational speed exceeds the inner rotational speed due to ignition of the engine (in an overrun state). An inclined surface is formed to guide the roller in a direction to lift the roller.
According to this configuration, when the roller is centrifuged from the outer peripheral surface of the inner, the roller can be held between the inclined surface formed in the inertial body and the inner peripheral surface of the cam chamber. The fluttering can be suppressed and the behavior of the roller can be stabilized, contributing to the improvement of the clutch performance.

(Invention of Claim 4)
4. The torque transmission device for starting an engine according to claim 1, wherein the inertial body is formed with a roller storage space for storing the roller and a spring receiving surface for receiving a load of the spring. Is provided with a roller pressing portion for transmitting the load of the spring to the roller.
According to said structure, an inertial body can be manufactured easily and cheaply by press work etc., for example.

(Invention of Claim 5)
In the engine starting torque transmission device according to claim 4, the inertial body is an annular body that is continuous in the circumferential direction, and the inner circumferential side of the inertial body that faces the outer circumferential surface of the inner is provided with a roller. A rubber is attached to each outer side in the axial direction in a ring shape, and when the inertial body moves in the circumferential direction in conjunction with the movement of the roller, the rubber slides on the outer peripheral surface of the inner.
By causing the rubber mounted on the entire inner circumference side of the inertial body to slidably contact the outer circumferential surface of the inner, the outflow of the lubricant (for example, grease) filled in the clutch can be suppressed. As a result, the lubricity between the roller and the inner can be maintained well, and the wear of the roller can be reduced. Further, the rubber of the present invention can be used as an indirect part described in claim 2. That is, since sliding resistance is generated when the rubber and the inner are in sliding contact with each other, the separation rotational speed of the clutch can be reduced as in the second aspect of the invention.

  The best mode for carrying out the present invention will be described in detail with reference to the following examples.

FIG. 1 is a half sectional view of an engine starting torque transmission device 1.
The engine starting torque transmission device (hereinafter abbreviated as “torque transmission device 1”) of the present embodiment is driven by a starter 2 (see FIG. 5) to rotate and a crankshaft 4 of the engine. The second rotating body 5 is fixed to (see FIG. 1), and the one-way clutch 6 that interrupts transmission of torque between the first rotating body 3 and the second rotating body 5 and the like.
The torque transmission device 1 is applied to, for example, an engine automatic stop / restart system that automatically controls engine stop and restart. This system, for example, automatically stops the engine when it stops at a red light at an intersection or when it stops due to traffic jams, etc., and then responds to a predetermined start operation (for example, when the driver releases the brake pedal) The system automatically restarts the engine, and is generally called an idle stop system, an eco-run system, or the like.

The first rotating body 3 is a ring gear having a ring shape in which a cylindrical hole is formed in a central portion in the radial direction, and a tooth portion 3a is continuously formed on the entire outer periphery. A starter is provided on the tooth portion 3a. The two pinion gears 7 (see FIG. 5) are always meshed.
The second rotating body 5 is, for example, a flywheel for an MT vehicle or a drive plate for an AT vehicle, and a ring-shaped boss portion 5a is provided at a central portion in the radial direction. As shown in FIG. 1, the end of the crankshaft 4 protruding from the side wall of the engine block 8 is fixed with bolts 9.

As shown in FIG. 1, the first rotating body 3 and the second rotating body 5 are disposed close to each other in the axial direction, and the inner peripheral surface of a cylindrical hole formed in the first rotating body 3, The two are assembled so as to be relatively rotatable via a bearing 10 disposed between the outer peripheral surface of the boss portion 5 a provided on the rotating body 5. The bearing 10 is, for example, a ball bearing with a seal.
The clutch 6 is incorporated in the first rotating body 3 together with a seal part 11 (described below). The first rotating body 3 has a recess formed in a side surface facing the second rotating body 5 in the axial direction, a clutch space in which the clutch 6 is disposed in the recess, and a seal component 11 on the radially outer side of the clutch 6. And a seal space to be arranged is set.

The seal component 11 is, for example, a well-known oil seal (see FIG. 1), and is press-fitted into a seal space of a recess formed in the first rotating body 3 (a space formed on the radially outer side of the clutch 6). The first rotating body 3 is assembled so as not to rotate. The seal part 11 has a rubber lip portion 11 a, and the lip portion 11 a is pressed against the outer peripheral surface of the clutch 6 to respond to relative rotation between the first rotating body 3 and the second rotating body 5. Thus, the lip portion 11 a is in sliding contact with the outer peripheral surface of the clutch 6 to prevent the grease from flowing out from the clutch 6.
The inner peripheral side of the clutch 6 is sealed by the bearing 10 (a ball bearing with a seal).

Next, the configuration of the clutch 6 according to the present invention will be described in detail.
As shown in FIG. 1, the clutch 6 includes an inner 12 provided integrally with the first rotating body 3, an outer 13 that is press-fitted and fixed to the second rotating body 5, and an inner 12 and an outer 13. When the roller 15 disposed in the formed cam chamber 14 (see FIG. 2), the spring 16 that directly or indirectly presses the roller 15, and the roller 15 moves in the circumferential direction of the cam chamber 14, An inertial body (hereinafter referred to as a retainer 17) that moves integrally with the roller 15 is provided.
The inner 12 is formed on the radially inner side of a recess that forms a clutch space and a seal space in the first rotating body 3, and forms a circular outer peripheral surface.

The outer 13 is integrally provided with a press-fit portion 13 a extending in the axial direction, and an outer peripheral surface of the press-fit portion 13 a is provided with a predetermined tightening margin on an inner peripheral surface of a press-fit hole portion formed in the second rotating body 5. Is press-fitted and fixed. The outer peripheral surface of the outer 13 is formed as a seal surface on which the lip portion 11a of the seal component 11 is slidably contacted, and the seal surface (the outer peripheral surface of the outer 13) and the outer peripheral surface of the press-fit portion 13a are the same surface with no step. Is formed by.
As shown in FIG. 2, the cam chamber 14 is formed between the cam surface formed on the inner periphery of the outer 13 and the outer periphery of the inner 12. The cam chamber 14 is provided in a wedge shape in which the space gradually narrows from one end side (the right side in the drawing) to the other end side (the left side in the drawing), and one end side in the circumferential direction has a diameter of the roller 15. The other end side in the circumferential direction is formed narrower than the diameter of the roller 15.

A spring chamber 18 that houses the spring 16 is continuously formed at one end of the cam chamber 14. The spring 16 presses the roller 15 via the retainer 17 in the other end side of the cam chamber 14, that is, in a direction in which the space of the cam chamber 14 becomes narrower. In the following description, the direction in which the space of the cam chamber 14 is narrowed is referred to as a wedge direction, and the direction in which the space of the cam chamber 14 is widened is referred to as an anti-wedge direction.
The retainer 17 is formed, for example, in a substantially U shape and is disposed so as to surround the periphery of the roller 15. That is, the roller 15 is disposed inside the substantially U-shape. However, as shown in FIG. 2, the retainer 17 is arranged in a state where both sides of the roller 15 in the radial direction are sandwiched in the circumferential direction of the clutch 6. Accordingly, the retainer 17 moves in the same direction as the roller 15 in conjunction with the movement of the roller 15 when the roller 15 moves in the circumferential direction in the cam chamber 14.

Next, the operation and effect of the torque transmission device 1 will be described.
a) When starting the engine When the first rotating body 3 (ring gear) is driven and rotated by the starter 2, the clutch 6 is engaged. That is, when the inner 12 rotates integrally with the first rotating body 3 while the outer 13 is stationary, the roller 15 is pressed by the spring 16 integrally with the retainer 17 and moves in the wedge direction of the cam chamber 14. For this reason, the roller 15 is sandwiched between the cam surface of the outer 13 and the outer peripheral surface of the inner 12 to be locked. As a result, torque is transmitted in the order of first rotating body 3 → clutch 6 → second rotating body 5 (flywheel) → crankshaft 4 to start cranking.

  When the engine is ignited by the rotation of the crankshaft 4 and the acceleration of the engine is increased, as shown by the magnitude of the arrow shown in FIG. 3, an overrun state occurs in which the rotational speed of the outer 13 exceeds the rotational speed of the inner 12. . Even if the outer 13 rotates at a high speed at the moment of shifting to the overrun state, the rollers 15 and the retainer 17 are less likely to follow the rotation of the outer 13 due to the inertial mass of both the roller 15 and the retainer 17. That is, the roller 15 and the retainer 17 do not move following the rotation direction of the outer 13 (in the direction of the arrow in the figure), and try to stop on the spot. In other words, at the moment when the outer 13 rotates at a high speed, the roller 15 and the retainer 17 seem to move in the anti-wedge direction (the anti-arrow direction in the figure) of the cam chamber 14 against the load of the spring 16. The power (inertial force) of

Thereafter, as the outer 13 rotates, the roller 15 gradually moves integrally with the retainer 17 in the anti-wedge direction of the cam chamber 14, and the roller 15 is centrifuged from the outer peripheral surface of the inner 12 (the clutch 6 is idled). ). Thereby, since transmission of torque is interrupted between the first rotating body 3 and the second rotating body 5, the rotation of the engine is not transmitted to the starter 2.
According to the clutch 6 of the present embodiment, the roller 15 can be centrifuged from the outer peripheral surface of the inner 12 at a lower rotational speed (for example, lower than the idling speed) as compared with the conventional roller clutch without the retainer 17. As a result, the wear of the roller 15 can be greatly reduced, and the life of the clutch 6 can be improved.

  b) Also, if the engine is restarted immediately after a misfire, negative acceleration occurs in the engine. That is, the rotation of the outer 13 is rapidly decelerated. In this case, contrary to when the engine is ignited, an inertial force is applied to the roller 15 and the retainer 17 so as to move the cam chamber 14 in the wedge direction (the arrow direction shown in FIG. 4). That is, since the inertial force acts in the direction in which the spring 16 biases the roller 15, the first rotating body 3 is driven by the starter 2 as shown by the size of the arrow shown in FIG. When the speed exceeds the rotational speed of the outer 13, the roller 15 can move faster in the wedge direction of the cam chamber 14, and the clutch 6 can be engaged in a short time.

FIG. 6 is an enlarged sectional view showing a part of the clutch 6.
The clutch 6 according to the second embodiment is an example in which the retainer 17 is provided with an inclined surface 17a for guiding the roller 15 as shown in FIG. The inclined surface 17a is formed on a wall portion of the retainer 17 disposed on the anti-spring side of the roller 15, that is, on the wedge side (left side in the drawing) of the roller 15, and from the wall portion to the inner peripheral side (roller 15). And the outer peripheral surface of the inner 12).
According to the above configuration, when the roller 15 is centrifuged from the outer peripheral surface of the inner 12, the roller 15 can be held between the inclined surface 17 a formed on the retainer 17 and the inner peripheral surface of the cam chamber 14. The fluttering of the roller 15 centrifuged from 12 can be suppressed, and the behavior of the roller 15 can be stabilized. As a result, the uneven wear of the roller 15 can be suppressed and the operation of the clutch 6 can be performed reliably, so that the performance of the clutch 6 is improved.

FIG. 7A is a partially developed view of the retainer 17, and FIG. 7B is an enlarged sectional view showing a part of the clutch 6.
The clutch 6 according to the third embodiment is an example in which a retainer 17 that moves in conjunction with the movement of the roller 15 is formed in an annular body that is continuous in the circumferential direction. As shown in FIG. 7A, the retainer 17 is formed with a roller storage space 17 b that stores the roller 15 and a spring receiving surface 17 c that receives the load of the spring 16.
The roller storage spaces 17b are formed in a rectangular shape on the surface of the retainer 17, and are formed by the number of rollers 15 used in the clutch 6. One roller 15 is stored in each roller storage space 17b (see FIG. 8).

Further, the roller storage space 17b is provided with a roller pressing portion 17d for transmitting the load of the spring 16 to the roller 15 as shown in FIG. The roller pressing portion 17d is provided on the opposite wedge side (the right side in the figure) with respect to the roller 15, and is formed by cutting and raising from the surface of the retainer 17 at a substantially right angle.
The spring receiving surface 17c is provided at a plurality of locations in the circumferential direction of the retainer 17 at substantially equal intervals. The spring receiving surface 17c is formed by cutting and raising from the surface of the retainer 17 at a substantially right angle, like the roller pressing portion 17d.
As shown in FIG. 7B, the spring 16 is housed in a spring chamber 18 formed independently of the cam chamber 14 on the inner periphery of the outer 13, and indirectly wedges the roller 15 via the retainer 17. Energizing in the direction.

The number of spring chambers 18 may be the same as the number of rollers 15, but the clutch capacity may be set larger by reducing the number of rollers 15 and increasing the number of rollers 15 that can be used. Is also possible.
Also in the present embodiment, as in the first embodiment, when the clutch 6 shifts to the overrun state due to the ignition of the engine and the rotational speed of the outer 13 increases rapidly, the roller 15 and the retainer 17 are provided with the spring 16. The inertial force that tries to move in the anti-wedge direction of the cam chamber 14 works against the load. As a result, the roller 15 moves in the anti-wedge direction together with the retainer 17 at a lower rotational speed than the conventional roller clutch without the retainer 17 (for example, at an idling speed or less), and the roller 15 is centrifuged from the outer peripheral surface of the inner 12. It is possible to separate them.

Further, when the engine is restarted immediately after the misfire, the roller 15 and the retainer 17 are subjected to inertial force to move in the wedge direction of the cam chamber 14 as in the first embodiment. The chamber 14 can move faster in the wedge direction, and the clutch 6 can be quickly engaged.
The retainer 17 of the present embodiment is an annular body that is continuous in the circumferential direction, and processes such as drilling for forming the roller storage space 17b and cutting and raising for forming the roller pressing portion 17d and the spring receiving surface 17c. Can be manufactured easily and inexpensively by, for example, pressing.

FIG. 9 is an enlarged sectional view showing a part of the clutch 6.
As in the case of the third embodiment, the clutch 6 according to the fourth embodiment uses an annular retainer 17 that is continuous in the circumferential direction, and as shown in FIG. 9, a rubber ring is provided around the inner circumference of the retainer 17. 19 is mounted (for example, baked). As shown in FIG. 10, the rubber rings 19 are mounted on both outer sides in the axial direction (left and right direction in the drawing) of the roller 15, and are in sliding contact with the outer peripheral surface of the inner 12.
According to the above configuration, both outer sides in the axial direction of the roller 15 are sealed by the pair of rubber rings 19, that is, the rubber ring 19 can be used as a sealing component, so that the lubricant ( For example, the outflow of grease) can be suppressed. As a result, good lubricity between the roller 15 and the inner 12 can be maintained, and wear of the roller 15 can be reduced.

  Further, sliding the rubber ring 19 to the outer peripheral surface of the inner 12 causes a sliding resistance between the rubber ring 19 and the inner 12 when the inner 12 and the retainer 17 rotate relative to each other. This sliding resistance acts in a direction in which the roller 15 and the retainer 17 are less likely to follow the rotation of the outer 13 when the outer 13 rotates at a high speed due to the ignition of the engine. By cooperating with the dynamic resistance, the separation rotational speed of the clutch 6 can be further reduced, and the degree of freedom in design can be increased.

(Modification)
In the fourth embodiment, an example in which the rubber ring 19 is mounted on the inner periphery of the retainer 17 has been described. For example, an indirect part made of a material other than rubber is mounted on the entire inner periphery or a part of the inner periphery of the retainer 17. Then, the outer peripheral surface of the inner 12 may be slidably contacted. In this case, even if the indirect part cannot be provided with a sealing function, the effect of reducing the separation rotational speed of the clutch 6 by using the sliding resistance generated between the indirect part and the inner 12 can be expected.
In the third and fourth embodiments, the retainer 17 is described as an annular body that is continuous in the circumferential direction. For example, as described in the first embodiment, the retainer 17 mounted for each roller 15 (the embodiment) A rubber component or an indirect component other than rubber may be attached to the inner periphery of the inner periphery of the shape (in FIG.

It is a half sectional view of an engine starting torque transmission device. It is an expanded sectional view showing a part of clutch. It is a partial sectional view of a clutch for explaining the operation at the time of engine ignition. It is a partial cross section figure of the clutch explaining the action | operation at the time of restart after engine misfire. It is sectional drawing of a starter and the torque transmission apparatus for engine starting. (Example 2) which is an expanded sectional view which shows a part of clutch. (A) The partial expanded view of a retainer, (b) It is an expanded sectional view which shows a part of clutch (Example 3). (Example 3) which is sectional drawing (AA sectional drawing) which cut | disconnected a part of clutch in the radial direction. (Example 4) which is an expanded sectional view which shows a part of clutch. (Example 4) which is sectional drawing (BB sectional drawing) which cut | disconnected a part of clutch in the radial direction.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Engine starting torque transmission device 2 Starter 3 1st rotary body 3a Tooth part (gear part) of 1st rotary body
4 Engine crankshaft 5 Second rotating body 6 Clutch 7 Pinion gear 12 Inner 13 Outer 14 Cam chamber 15 Roller 16 Spring 17 Retainer (Inertial body)
17a Inclined surface formed on retainer 17b Roller storage space 17c Spring receiving surface 17d Roller pressing portion 19 Rubber ring (rubber, indirect member)

Claims (5)

An engine start torque transmission device for transmitting a drive torque generated by a starter to an engine crankshaft to start the engine,
A first rotating body having a gear portion that always meshes with the pinion gear of the starter;
A second rotating body that is assembled so as to be relatively rotatable with the first rotating body, and is fixed to the crankshaft and rotates integrally with the crankshaft;
Provided between the first rotating body and the second rotating body, and when the first rotating body rotates by being driven by the starter, the first rotating body rotates to the second rotating body. A one-way clutch that cuts off torque transmission from the second rotating body to the first rotating body when the second rotating body rotates by being driven by the engine. ,
The clutch includes an inner having a circular outer peripheral surface in the first rotating body, and an outer forming a wedge-shaped cam chamber between the outer periphery of the inner and the second rotating body; A roller disposed in the cam chamber, a spring that directly or indirectly presses the roller in a narrow direction of the cam chamber, and a relative rotation between the outer and the inner causes the roller to move to the cam chamber. And an inertial body that moves in the same direction as the roller when the roller is moved in the circumferential direction. The torque transmission device for starting an engine according to claim 1,
The inertial body is in sliding contact with the outer peripheral surface of the inner directly, or an indirect part is disposed between the inertial body and the inner, and indirectly through the indirect part with the outer peripheral surface of the inner. A torque transmission device for starting an engine characterized by being in sliding contact. In the engine starting torque transmission device according to claim 1 or 2,
The inertial body is formed with an inclined surface that guides the roller in a direction to lift the roller from the outer peripheral surface of the inner when the rotation speed of the outer exceeds the rotation speed of the inner due to ignition of the engine. A torque transmission device for starting an engine. The torque transmission device for starting an engine according to any one of claims 1 to 3,
The inertia body is formed with a roller storage space for storing the roller and a spring receiving surface for receiving the load of the spring, and a roller pressing portion for transmitting the load of the spring to the roller in the roller storage space. An engine starting torque transmission device is provided. In the engine starting torque transmission device according to claim 4,
The inertial body is an annular body that is continuous in the circumferential direction, and the inner circumferential side of the inertial body that faces the outer peripheral surface of the inner has a ring shape on both outer sides in the axial direction of the roller. A torque transmission device for starting an engine, wherein the rubber is slidably contacted with the outer peripheral surface of the inner when the inertial body moves in the circumferential direction in conjunction with the movement of the roller.

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