JP2012082732A - Starting device of internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a constantly meshing type starting device of an internal combustion engine which can improve fuel economy, durability and silence, while reducing cost.SOLUTION: The starting device includes a ring gear 11 for meshing with a pinion gear 6, a drive plate 12 integrally rotating with the ring gear 11, a driven plate 19 integrally rotating with a crankshaft 3, an engaging member 17 rockably installed on the driven plate 19, and an engaging object member 13 installed on the drive plate 12 and engaging with a tip part of the engaging member 17 when a rotating speed of the drive plate 12 is higher than a rotating speed of the driven plate 19. The tip part of the engaging member 17 rotates to separate from the rotational axis by centrifugal force by releasing engagement with the engaging object member 13 when the rotating speed of the driven plate 19 becomes higher than the rotating speed of the drive plate 12.

Description

  The present invention relates to a starting device for an internal combustion engine, and more particularly to a starting device for an internal combustion engine in which a pinion gear of a starter motor and a ring gear are always meshed.

  An internal combustion engine starter is configured such that a starter motor pinion gear meshes with a ring gear that transmits driving force to the crankshaft of the internal combustion engine, and the starter motor starts the internal combustion engine by driving the crankshaft via the pinion gear and the ring gear. Let In a conventional starter for an internal combustion engine, the crankshaft and the ring gear rotate together, and only when the driver turns on the starter switch at the start, the pinion gear is slid to engage the pinion gear and the ring gear. In such a starter for an internal combustion engine, there is a problem that when the meshing rate and the meshing accuracy between the gears are improved, the pinion gear is difficult to mesh with the ring gear at the time of starting, and the pinion gear is difficult to disengage from the ring gear after the starting. For this reason, a starter for an internal combustion engine having a one-way clutch that always meshes the pinion gear and the ring gear and allows only the transmission of the driving force from the ring gear to the crankshaft has been proposed (for example, Patent Documents 1 and 2). ). In such an internal combustion engine starter, the one-way clutch starts the internal combustion engine by transmitting the output torque of the starter motor to the crankshaft. Once the internal combustion engine is started, the one-way clutch runs idle, and the ring gear Remains stationary while meshing with the pinion gear of the starter motor. Hereinafter, such a mechanism in which the pinion gear and the ring gear are always meshed is referred to as a constant meshing mechanism.

  In Patent Document 1, a ring gear is provided between the internal combustion engine and the flywheel so as to be relatively rotatable via a bearing at the end of the output shaft of the internal combustion engine, and always meshes with the pinion gear of the starter motor. It has a connecting member connected to the end of the output shaft, has a one-way clutch that allows only transmission of rotational force from the ring gear to the rotating member, and has a seal member provided between the ring gear and the rotating member A starting device having another seal member provided between the ring gear and the internal combustion engine body and having a through-hole formed in the ring gear is disclosed. In this starting device, the bearing is lubricated by the lubricating oil (engine oil) supplied from the lubricating oil supply path of the internal combustion engine body, and the one-way clutch is lubricated through the through hole of the ring gear.

  In Patent Document 2, a crank gear of an internal combustion engine is provided between the internal combustion engine and the flywheel. The ring gear is supported on the internal combustion engine body through a bearing so as to be relatively rotatable, and always meshes with a pinion gear of a starter motor. A starting device is disclosed having a one-way clutch that has a support plate coupled to the ring and allows only transmission of rotational force from the ring gear to the support plate. In this starting device, the bearing and the one-way clutch are lubricated with grease instead of lubricating with lubricating oil (engine oil).

JP 2008-223704 A JP 2007-32498 A

  However, in the starting device described in Patent Document 1, since the bearing and the one-way clutch are lubricated with engine oil, the sliding surfaces of the seal member and other seal members, the seal member, and other seals are used to prevent oil leakage. Parts such as the mating surface of the member, the race surface of the one-way clutch, and the mating surface of the bearing need to be finished with high precision, resulting in high costs. In the starting device described in Patent Document 1, when the internal combustion engine is a diesel engine, the life of the bearing and the one-way clutch is significantly reduced by fine particles contained in the engine oil (soot generated during engine combustion).

  In the starting device described in Patent Document 2, the bearing and the one-way clutch are lubricated with grease. However, the deterioration of the grease itself causes problems such as seizure of the bearing and the one-way clutch, and the life of the bearing and the one-way clutch. Will be significantly reduced.

  Furthermore, in the starting device having a constant meshing mechanism using a one-way clutch as in Patent Documents 1 and 2, drag torque is generated during idling in the one-way clutch, and the fuel consumption of the engine deteriorates due to the drag torque. There is a risk of rattling noise between the pinion gear and the ring gear.

  A main object of the present invention is to provide a starter for a constantly meshing internal combustion engine that can improve fuel efficiency, durability, and quietness while reducing costs.

  In one aspect of the present invention, in a starting device for an internal combustion engine, a pinion gear attached to an output shaft of a starter, a ring gear meshing with the pinion gear, a drive plate that rotates integrally with the ring gear, and a crankshaft of the internal combustion engine A driven plate that rotates integrally, at least one engaging member that is swingably attached to the driven plate, and a position that is attached to the drive plate and closer to the rotational axis of the drive plate than the engaging member And an engaged member that engages with the distal end portion of the engaging member when the rotational speed of the drive plate is higher than the rotational speed of the driven plate, and the distal end of the engaging member The rotational speed of the driven plate is greater than the rotational speed of the drive plate Becomes higher, the are disengaged from the engaged member, characterized by turning away from the axis of rotation of the drive plate by centrifugal force.

  In the internal combustion engine starter according to the present invention, the starter of the engagement member includes at least one biasing member that biases the distal end of the engagement member so as to approach the rotation axis of the drive plate. When the rotational speed of the driven plate becomes higher than the rotational speed of the drive plate, the engagement with the engaged member is released, and the centrifugal force applied to the distal end portion of the engaging member is applied to the biasing member. It is preferable to rotate away from the rotational axis of the drive plate by exceeding the force.

  In the internal combustion engine starter according to the present invention, the engaged member is formed in a substantially annular shape, and a plurality of groove portions recessed at predetermined intervals on the outer peripheral surface of the engaged member are formed, It is preferable that one of the circumferential surfaces of each of the groove portions has an engaged surface that engages with the distal end portion of the engaging member.

  In the starter for an internal combustion engine according to the present invention, it is preferable that the groove is a curved surface and is smoothly connected to the engaged surface.

  In the internal combustion engine starter according to the present invention, there are two or more engaging members, and at least one of the plurality of engaging members is one of the corresponding plurality of engaged surfaces. When engaged, it is preferable that other engaging members are not engaged with the engaged surface.

  In the internal combustion engine starter according to the present invention, the contact point between the engagement member and the non-engagement surface when the engagement member is engaged with the engaged surface is generated when the internal combustion engine is started. It is preferable that it is arranged on the same line as the load direction.

  In the internal combustion engine starter according to the present invention, a load direction generated when starting the internal combustion engine is a direction of a tangent of a circle passing through a contact point between the engagement member and the engaged surface, and the tangent is It is preferable that the contact point between the engagement member and the engaged surface passes through the rotation shaft of the engagement member.

  In the internal combustion engine starter according to the present invention, the engagement member has a stopper portion, and the driven plate rotates so that a tip end portion of the engagement member is separated from a rotation axis of the drive plate. It is preferable to have another stopper portion for locking the stopper portion.

  The starter for an internal combustion engine according to the present invention includes at least one support plate attached to the driven plate, and the engagement member is disposed between the driven plate and the support plate, and the driven It is preferable that the plate and the support plate are swingably attached.

  In the internal combustion engine starter according to the present invention, it is preferable that the engaging member has a buffer portion made of a buffer material on a surface of a portion that can come into contact with the engaged member.

  In the internal combustion engine starter according to the present invention, it is preferable that the engaged member has a buffer portion made of a buffer material on a surface of a portion that can come into contact with the engaging member.

  In the internal combustion engine starter according to the present invention, the engaged member includes a damper that is rotatably attached to the drive plate and cushions torsion between the drive plate and the engaged member. preferable.

  In the internal combustion engine starter according to the present invention, the damper includes a housing portion formed in the engaged member, a support member fixed to the drive plate and inserted into the housing portion, and the housing portion. It is preferable to provide a cushioning material disposed between an end surface in the circumferential direction of the support member and the support member.

  In the internal combustion engine starter according to the present invention, the engagement member is attached to the driven plate so as to be rotatable in the same direction as the rotation direction of the driven plate, and the torsion between the engagement member and the driven plate is performed. It is preferable to provide a damper for buffering.

  In the internal combustion engine starter according to the present invention, the damper is rotatably supported by the driven plate, and the engagement member is swingably attached to the center plate, and the center plate and the driven plate. It is preferable to provide an elastic member that cushions the twist between the two.

  In the internal combustion engine starter according to the present invention, the engaging member may have a damper that absorbs shock when the tip is engaged with the engaged member, while the tip is extendable. preferable.

  In the internal combustion engine starter according to the present invention, the engaging member is attached to the driven plate so as to be swingable and has an end portion, and is attached to the end member so as to be slidable and to be engaged. It is preferable to include a tip member that can be engaged with the member, and an elastic member that is housed in the housing portion and is disposed between the tip member and the end member in the sliding direction of the tip member.

  In the internal combustion engine starter according to the present invention, it is preferable that one end is fixed to the driven plate, and the other end includes a pin member that supports the engaging member in a swingable manner.

  In the internal combustion engine starter according to the present invention, the internal combustion engine has a cylindrical portion that extends in the axial direction at a portion farther from the rotation axis of the drive plate than the crankshaft on the outer surface, One of the drive plate and the engaged member is preferably rotatably supported by the cylindrical portion.

  The starter for an internal combustion engine according to the present invention preferably includes a bush attached to the cylindrical portion and bearings one of the drive plate and the engaged member.

  The starter for an internal combustion engine of the present invention preferably includes a ball bearing attached to the cylindrical portion and bearings one of the drive plate and the engaged member.

  In the internal combustion engine starter according to the present invention, a ring member that is arranged concentrically with the rotating shaft of the engaging member and rotates integrally with the engaging member, and concentrically with the rotating shaft of the drive plate. And another ring member that rotates integrally with the drive plate, and the ring member frictionally engages with the other ring member at a corner portion of an outer peripheral surface, and a tip end portion of the engagement member When the rotational speed of the driven plate becomes higher than the rotational speed of the drive plate, the frictional force between the ring member and the other ring member causes the drive plate to move away from the rotational axis of the drive plate by a predetermined distance. Preferably it is maintained.

  In the internal combustion engine starter according to the present invention, the ring member avoids contact between the ring member and the other ring member when the internal combustion engine is started at a part of the corner portion of the outer peripheral surface. It is preferable to have a notch portion.

  In the internal combustion engine starter according to the present invention, the drive plate has a contact portion capable of contacting the engagement member, and the engagement member is slidable with the contact portion of the drive plate. A friction part generated between the sliding part and the contact part when the rotational speed of the driven plate is higher than the rotational speed of the drive plate. It is preferable that the force plate is maintained at a position away from the rotation axis of the drive plate by a predetermined distance.

  The internal combustion engine starter according to the present invention includes a ring member that is arranged concentrically with a rotation shaft of the drive plate and rotates integrally with the engagement member, and the engagement member slides with the ring member. A movable sliding portion, and a tip portion of the engaging member is generated between the sliding portion and the ring member when a rotational speed of the driven plate is higher than a rotational speed of the drive plate. It is preferable that the friction plate be maintained at a position away from the rotational axis of the drive plate by a predetermined distance.

  According to the present invention, the starter does not use a one-way clutch, but uses an engagement mechanism that can engage an engagement member and an engaged member, so that no lubrication is required and there are few high-precision finished surfaces. The cost of the apparatus can be reduced. Moreover, since an expensive one-way clutch is not required, cost can be reduced and lubrication is not required, so that the degree of freedom in design is increased. In addition, since the engagement member and the engaged member are completely separated when the engagement is released in the engagement mechanism, the problem of drag torque unlike the one-way clutch does not occur, the fuel consumption of the engine improves, and the pinion gear and the ring gear The generation of rattling noise can be eliminated. In addition, since the engaging member and the engaged member are completely separated when the engagement is released in the engaging mechanism, dragging after starting the engine like a one-way clutch is eliminated, and the durability of the apparatus can be improved. In addition, the engagement mechanism in which the engagement member and the engaged member are completely separated when the engagement is released can be applied to a diesel vehicle because it does not require lubrication. Furthermore, since the operation of the engagement mechanism does not depend on friction, it can operate without being affected by changes in the friction coefficient, and has excellent resistance to foreign matters.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a plan view seen from an axial direction schematically showing the configuration of a starting device for an internal combustion engine according to Embodiment 1 of the present invention. FIG. 2 is a cross-sectional view taken along the line XX ′ of FIG. 1 schematically showing the configuration of the starting device for the internal combustion engine according to the first embodiment of the present invention. It is the top view seen from the axial direction for demonstrating the operation | movement during starting of the starting device of the internal combustion engine which concerns on Example 1 of this invention. It is the top view seen from the axial direction for demonstrating the operation | movement after starting cancellation | release of the starting device of the internal combustion engine which concerns on Example 1 of this invention. It is sectional drawing which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 2 of this invention. It is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 3 of this invention. It is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 4 of this invention. It is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 5 of this invention. It is the top view seen from the axial direction which showed typically the composition of the claw member in the starting device of the internal-combustion engine concerning Example 6 of the present invention. It is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 7 of this invention. FIG. 11 is a cross-sectional view taken along the line XX ′ of FIG. 10 schematically showing the configuration of an internal combustion engine starter according to Embodiment 7 of the present invention. It is the top view seen from the axial direction which showed typically the structure of the starter of the internal combustion engine which concerns on Example 8 of this invention. FIG. 13 is a partial cross-sectional view taken along the line XX ′ of FIG. 12 schematically showing the configuration of an internal combustion engine starter according to Embodiment 8 of the present invention. FIG. 13 is a partial cross-sectional view taken along line YY ′ of FIG. 12 schematically showing the configuration of the starter for an internal combustion engine according to Example 8 of the present invention. It is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 9 of this invention. It is sectional drawing which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 10 of this invention. It is the top view seen from the arrow A of FIG. 16 which showed typically the structure of the driven plate in the starting device of the internal combustion engine which concerns on Example 10 of this invention. It is the top view seen from the arrow A of FIG. 16 which showed typically the structure of the side plate in the starting device of the internal combustion engine which concerns on Example 10 of this invention. It is the top view seen from the arrow A of FIG. 16 which showed typically the structure of the center plate in the starting device of the internal combustion engine which concerns on Example 10 of this invention. It is sectional drawing which showed typically the structure of the claw member in the starter of the internal combustion engine which concerns on Example 11 of this invention. It is sectional drawing which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 12 of this invention. It is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 13 of this invention. It is sectional drawing between XX 'of FIG. 22 which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 13 of this invention. It is the top view seen from the axial direction for demonstrating the operation | movement after starting cancellation | release of the starting device of the internal combustion engine which concerns on Example 13 of this invention. It is the top view seen from the axial direction which showed typically the structure of the claw member in the starting device of the internal combustion engine which concerns on Example 13 of this invention, and sectional drawing between YY 'in a top view. It is the top view seen from the axial direction which showed typically the structure of the starter of the internal combustion engine which concerns on Example 14 of this invention. It is sectional drawing between XX 'of FIG. 26 which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 14 of this invention. It is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 15 of this invention. It is sectional drawing between XX 'of FIG. 28 which showed typically the structure of the starter of the internal combustion engine which concerns on Example 15 of this invention.

  In an internal combustion engine starter according to an embodiment of the present invention, a pinion gear (6 in FIG. 2) attached to an output shaft of a starter, a ring gear (11 in FIGS. 1 and 2) meshing with the pinion gear, and the ring gear A drive plate (12 in FIGS. 1 and 2) that rotates integrally, a driven plate (19 in FIG. 2) that rotates integrally with a crankshaft (3 in FIGS. 1 and 2) of the internal combustion engine, and the driven plate At least one engaging member (17 in FIGS. 1 and 2) attached so as to be swingable, and attached to the drive plate, and disposed closer to the rotational axis of the drive plate than the engaging member. And when the rotational speed of the drive plate is higher than the rotational speed of the driven plate, it is rotated so as to approach the rotational axis of the drive plate. And an engaged member (13 in FIGS. 1 and 2) that engages with the distal end of the engaging member. The distal end of the engaging member has a rotational speed of the driven plate of the drive plate. When it becomes higher than the rotational speed, the engagement with the engaged member is released, and it is rotated away from the rotational axis of the drive plate by centrifugal force.

  Note that, in the present application, where reference numerals are attached to the drawings, these are only for the purpose of helping understanding, and are not intended to be limited to the illustrated embodiments.

  An internal combustion engine starter according to Embodiment 1 of the present invention will be described with reference to the drawings. FIG. 1 is a plan view of an internal combustion engine starter according to Embodiment 1 of the present invention, as viewed from the axial direction schematically showing the configuration of the starter. FIG. 2 is a cross-sectional view taken along the line XX ′ in FIG. 1 schematically illustrating the configuration of the starting device for the internal combustion engine according to the first embodiment of the present invention. In FIG. 1, the flywheel 5 and the driven plate 19 in FIG. 2 are omitted.

  The starting device 1 is a device that starts an engine (not shown), and a driving force applied to a pinion gear 6 that rotates integrally with an output shaft (not shown) of a starter motor (not shown) and a crankshaft 3 of the engine. Is a constant-meshing type starting device that is always meshed with the ring gear 11 for transmitting the power. The starter 1 is disposed between an engine (not shown) and the flywheel 5. As a mechanism that replaces the one-way clutch, the starter 1 rotates the drive plate 12 when the engine is started, so that the claw member 17 is hooked on the hooking surface 13b of the rack member 13, and the rotational power is transmitted from the drive plate 12 to the driven plate 19. When the rotational speed of the driven plate 19 exceeds the rotational speed of the drive plate 12, the catch between the claw member 17 and the hooking surface 13 b of the rack member 13 is released, and the rotational power between the drive plate 12 and the driven plate 19 is reduced. It has a hooking mechanism (power transmission mechanism, ratchet mechanism, engagement mechanism) in which transmission is not performed.

  The hook mechanism is configured such that the end portion of the claw member 17 is rotatably attached to the driven plate 19 via the pin member 18, and the front end portion of the claw member 17 is urged radially inward by a spring 20. The member 13 rotates integrally with the drive plate 12. When the engine is started, the hooking mechanism rotates the drive plate 12 so that the hooking surface 13b of the rack member 13 approaches the tip of the claw member 17 and is hooked on the tip of the claw member 17. Rotational power is transmitted to the driven plate 19. When the rotational speed of the driven plate 19 exceeds the rotational speed of the drive plate 12, the hooking mechanism separates the hooking surface 13 b of the rack member 13 from the tip of the claw member 17, and the centrifugal force applied to the tip of the claw member 17. Exceeds the urging force of the spring 20, the tip of the claw member 17 jumps outward in the radial direction, the hook between the claw member 17 and the hooking surface 13 b of the rack member 13 is released, and the drive plate 12 and the driven plate 19 Rotational power is not transmitted between the two.

  When the claw member 17 is engaged with the hooking surface 13b, the starter 1 is connected to the crankshaft from the ring gear 11 via the drive plate 12, the rack member 13, the claw member 17, the pin member 18, the driven plate 19, and the bolt 4. When the claw member 17 is disengaged from the hooking surface 13b, the claw member 17 and the hooking surface 13b are cut off, and the driving force is transmitted from the ring gear 11 to the crankshaft 3. Absent.

  The starting device 1 includes, as main components, a cylinder block cylindrical portion 2, a crankshaft 3, a bolt 4, a flywheel 5, a pinion gear 6, a ring gear 11, a drive plate 12, a rack member 13, A bush 14, a stopper plate 15, a bolt 16, a claw member 17, a pin member 18, a driven plate 19, a spring 20, a spring stopper fitting 21, and a pin member 22 are included.

  The cylinder block cylindrical portion 2 is a cylindrical portion provided in a structure (cylinder block) serving as a skeleton of the engine. The cylinder block cylindrical portion 2 extends toward the flywheel 5 at the outer peripheral portion than the crankshaft 3. The inner peripheral surface of the cylinder block cylindrical portion 2 is separated from the crankshaft 3. The cylinder block cylindrical portion 2 is provided with a step portion for providing the bush 14 on the outer peripheral surface. The cylinder block cylindrical portion 2 rotatably supports a rack member 13 (including a drive plate 12 and a ring gear 11 that rotate integrally with the rack member 13) via a bush 14. A plurality of stopper plates 15 for restricting axial movement of the bush 14 and the rack member 13 (including the drive plate 12 and the ring gear 11 rotating integrally with the rack member 13) are provided at the tip of the cylinder block cylindrical portion 2. The bolts 16 are attached (six in FIG. 1).

  The crankshaft 3 is an output shaft of the engine and is rotatably supported by the cylinder block. A flywheel 5 and a driven plate 19 are fastened to the end of the crankshaft 3 by bolts 4. The crankshaft 3 rotates integrally with the flywheel 5 and the driven plate 19.

  The bolt 4 is a member for fastening the flywheel 5 and the driven plate 19 to the end of the crankshaft 3.

  The flywheel 5 is an annular member made of cast iron. The flywheel 5 is fixed to the crankshaft 3 together with the driven plate 19 by bolts 4, and rotates integrally with the crankshaft 3 and the driven plate 19. The flywheel 5 is arranged on the opposite side of the driven plate 19 to the cylinder block side (left side in FIG. 2). The flywheel 5 transmits rotational power toward a clutch (not shown).

  The pinion gear 6 is a drive gear that drives the ring gear 11. The pinion gear 6 is a spur gear (having a helical gear or a helical gear) which has fewer teeth than the ring gear 11, and is always meshed with the ring gear 11. The pinion gear 6 is attached to an output shaft of a starter motor (not shown) that starts an engine (not shown), and rotates integrally with the output shaft.

  The ring gear 11 is a driven gear to which the rotational torque of a starter motor (not shown) is transmitted via the pinion gear 6. The ring gear 11 is a spur gear (a helical gear or a helical gear may be used) having more teeth than the pinion gear 6. The ring gear 11 is always meshed with the pinion gear 6 on the outer peripheral surface. The ring gear 11 is fixed to the cylindrical portion 12 a on the outer periphery of the drive plate 12 on the inner peripheral surface, and rotates integrally with the drive plate 12.

  The drive plate 12 is an annular plate for rotationally driving the hooking mechanism. The drive plate 12 has a cylindrical cylindrical portion 12a extending in the axial direction on the outer peripheral portion. A ring gear 11 is fixed to the outer peripheral surface of the cylindrical portion. The drive plate 12 is fixed to the rack member 13 at the inner peripheral portion. The drive plate 12 rotates integrally with the ring gear 11 and the rack member 13. The drive plate 12 is rotatably supported by the cylinder block cylindrical portion 2 via the rack member 13 and the bush 14. In addition, the drive plate 12 is not only rotatably supported by the cylinder block cylindrical portion 2, but can also be rotated so that the outer peripheral surface is at a fixed position even if it is rotated like the crankshaft 3, the flywheel 5 or the like. It is good also as a structure supported by.

  The rack member 13 is a substantially annular member that can be hooked with the tip of the claw member 17 and is a constituent member of the hook mechanism. The rack member 13 is formed with a plurality of (eight in FIG. 1) groove portions 13a that are periodically recessed on the outer peripheral surface, and one end of the circumferential surface of the groove portion 13a has a tip portion of the claw member 17 and It has a plurality of (8 in FIG. 1) hooking surfaces 13b that can be engaged. The groove 13a has a curved surface and is smoothly connected to the hooking surface 13b. As a result, torque is smoothly transmitted from the rack member 13 to the claw member 17 when the rack member 13 and the claw member 17 are hooked, and the hitting sound (collision sound) at the time of hooking can be reduced. The hooking surface 13b is hooked with the tip of the claw member 17 when the rotational speed of the drive plate 12 is higher than the rotational speed of the driven plate 19 at the time of starting the engine. The rack member 13 is rotatably supported by the cylinder block cylindrical portion 2 via the bush 14. The inner peripheral portion of the rack member 13 is disposed between the side wall surface of the step portion of the cylinder block cylindrical portion 2 and the stopper plate 15 via the flange portions of the bushes 14 disposed on both sides in the axial direction. The axial movement is restricted by the side wall surface of the stepped portion of the block cylindrical portion 2 and the stopper plate 15.

  The bush 14 is a sliding bearing for rotatably supporting the drive plate 12 on the cylinder block cylindrical portion 2. The bush 14 has flange portions at both ends in the axial direction. The bush 14 is disposed between the side wall surface of the stepped portion of the cylinder block cylindrical portion 2 and the stopper plate 15, and the shaft of the drive plate 12 is formed by the side wall surface of the stepped portion of the cylinder block cylindrical portion 2 and the stopper plate 15. Directional movement is restricted.

  The stopper plate 15 is an annular plate that restricts the axial movement of the rack member 13 and the bush 14 disposed in the step portion of the cylinder block cylindrical portion 2. The stopper plate 15 is fixed to the distal end portion of the cylinder block cylindrical portion 2 by a plurality of (six in FIG. 1) bolts 16.

  The bolt 16 is a member for fastening the stopper plate 15 to the tip of the cylinder block cylindrical portion 2.

  The claw member 17 is a claw-shaped member that can be engaged with the hooking surface 13b of the rack member 13, and is a constituent member of the hook mechanism. The claw member 17 is disposed on the outer side in the radial direction than the rack member 13, and overlaps the rack member 13. The claw member 17 is swingably attached to a pin member 18 whose end is fixed to the driven plate 19. The claw member 17 can swing around the pin member 18 as a rotation axis. The claw member 17 is hooked on the hooking surface 13b of the rack member 13 when the tip portion is bounced down radially inward. The claw member 17 is urged by the spring 20 so that the tip end portion rotates inward in the radial direction. When the driven plate 19 is rotating, the claw member 17 jumps outward in the radial direction by the centrifugal force applied to the tip overcoming the urging force of the spring 20.

  The tip of the claw member 17 is urged radially inward by the spring 20 when the engine is started, and is in contact with the groove 13a of the rack member 13, and the drive plate 12 rotates to engage the hooking surface of the rack member 13. I get caught in 13b. When the tip of the claw member 17 is caught on the hooking surface 13 b of the rack member 13, the tips of the two claw members 17 are hooked simultaneously. When the tip of the claw member 17 is hooked on the hooking surface 13 b of the rack member 13, the rotational power of the drive plate 12 is supplied to the crankshaft 3 via the rack member 13, claw member 17, pin member 18, driven plate 19, and bolt 4. Is transmitted to.

  When the rotational speed of the driven plate 19 (crankshaft 3) becomes higher than the rotational speed of the drive plate 12 (ring gear 11) by starting the engine, the tip of the claw member 17 is separated from the hooking surface 13b of the rack member 13, When the centrifugal force related to the distal end portion of the member 17 exceeds the urging force of the spring 20, the spring 17 jumps outward in the radial direction, and the hooking with the hooking surface 13b of the rack member 13 is completely released. By releasing the hook between the tip of the claw member 17 and the hooking surface 13b of the rack member 13, the driving force is not transmitted from the ring gear 11 to the crankshaft 3.

  The pin member 18 is a member for attaching the claw member 17 to the outer peripheral portion of the driven plate 19 so as to be swingable. One end of the pin member 18 is fixed to the driven plate 19 and the other end supports the claw member 17 so as to be swingable.

  The driven plate 19 is an annular plate that can be rotationally driven by the drive plate 12 via the rack member 13, the claw member 17, and the pin member 18. The driven plate 19 is fixed to the crankshaft 3 together with the flywheel 5 by bolts 4, and rotates integrally with the crankshaft 3 and the flywheel 5. The driven plate 19 extends radially outward from the rack member 13, and one end of a plurality of (two in FIG. 1) pin members 18 is fixed at the outer peripheral portion. The claw member 17 is supported so as to be swingable.

  The spring 20 is an elastic member that biases the distal end portion of the claw member 17 radially inward. The spring 20 is supported by the pin member 22, one end is supported or fixed to the spring stopper metal 21, and the other end biases the claw member 17 so that the tip end portion of the claw member 17 rotates inward in the radial direction.

  The spring stopper fitting 21 is a fitting that supports one end of the spring 20. The spring stopper fitting 21 is fixed to the other end of the pin member 22 and is fixed to the driven plate 19 via the pin member 22. The spring stopper fitting 21 also serves as a detent stopper when the tip of the claw member 17 is flipped up.

  The pin member 22 is a pin-shaped member for supporting and fixing the spring 20 and the spring stopper fitting 21 to the driven plate 19. One end of the pin member 22 fixes the driven plate 19, the other end fixes the spring stopper fitting 21, and supports the spring 20 at the intermediate portion.

  Next, the operation of the internal combustion engine starter according to Embodiment 1 of the present invention will be described with reference to the drawings. FIG. 3 is a plan view seen from the axial direction for explaining the operation during start-up of the internal combustion engine starter according to Embodiment 1 of the present invention. FIG. 4 is a plan view seen from the axial direction for explaining the operation after the start cancellation of the starter for the internal combustion engine according to the first embodiment of the present invention.

  When the engine is stopped, as shown in FIG. 1, the tip of the claw member 17 is urged radially inward by the spring 20, contacts the groove 13a of the rack member 13, and is away from the hooking surface 13b.

  When the engine is started, the drive plate 12 is rotated via the pinion gear 6 and the ring gear 11 by the rotation of the starter motor. At this time, since the rack member 13 fixed to the drive plate 12 also rotates, the tip of the claw member 17 gradually changes its angle around the pin member 18 while sliding with the groove 13a of the rack member 13. .

  When the rack member 13 further rotates, the front end portion of the claw member 17 and the hooking surface 13b of the rack member 13 are hooked (engaged), and the state shown in FIG. 3 is obtained. In this state, as the drive plate 12 rotates, the crankshaft 3 starts to rotate via the rack member 13, the claw member 17, the pin member 18, the driven plate (19 in FIG. 2), and the bolt 4. When the rotational torque of the starter motor is transmitted to the crankshaft 3, the engine is triggered by this rotational torque.

  The engine starts and the driven plate 19 (crankshaft 3) starts to rotate at a speed higher than the drive plate 12 (ring gear 11). As the driven plate 19 rotates, the tip of the claw member 17 moves away from the hooking surface 13b of the rack member 13, and the claw member 17 held so as to be swingable by the pin member 18 has a tip that is radially outward by centrifugal force. Jumps up. As a result, the drive plate 12 and the driven plate 19 are completely cut off, resulting in a state as shown in FIG.

  When the engine is stopped and the engine speed is reduced, the tip of the claw member 17 that has been springed up by the centrifugal force springs down by the spring 20 and returns to the state shown in FIG.

  According to the first embodiment, the starter does not use a one-way clutch, and uses a hook mechanism that can engage the claw member 17 and the rack member 13, so that no lubrication is required and there are few high-precision finished surfaces. The cost can be reduced. Moreover, since an expensive one-way clutch is not required, cost can be reduced and lubrication is not required, so that the degree of freedom in design is increased. In addition, since the hook member 17 and the rack member 13 are completely separated when the engagement is released in the hook mechanism, the problem of drag torque unlike the one-way clutch does not occur, the fuel efficiency of the engine is improved, and the pinion gear 6 and the ring gear 11 The generation of rattling noise can be eliminated. Further, when the hook is released in the hook mechanism, the claw member 17 and the rack member 13 are completely separated from each other, so that the drag after the engine start like the one-way clutch is eliminated, and the durability of the apparatus can be improved. In addition, the hooking mechanism in which the claw member 17 and the rack member 13 are completely separated when the hook is released can be applied to a diesel vehicle because it does not require lubrication. Further, since the operation of the hooking mechanism does not depend on friction, it can operate without being affected by the change of the friction coefficient, and has excellent resistance to foreign matters. Furthermore, since the tip of the claw member 17 can be surely springed down by the spring 20, it is possible to ensure a reliable engine start.

  An internal combustion engine starter according to Embodiment 2 of the present invention will be described with reference to the drawings. FIG. 5 is a cross-sectional view schematically showing the configuration of the internal combustion engine starter according to Embodiment 2 of the present invention. 5 is a cross-sectional view corresponding to the line XX ′ in FIG. 1 in FIG.

  The second embodiment is a modification of the first embodiment, and an object to be supported by the cylinder block cylindrical portion 2 via the bush 14 is not the rack member 13 but the drive plate 12. The configuration excluding the drive plate 12 and the rack member 13 is the same as that of the first embodiment.

  The drive plate 12 has a cylindrical cylindrical portion 12b that extends toward the flywheel 5 on the inner peripheral portion. The cylindrical portion 12b is rotatably supported on the cylinder block cylindrical portion 2 via the bush 14 on the inner peripheral surface. The rack member 13 is fixed to the drive plate 12 on the outer periphery of the cylindrical portion 12b. The cylindrical portion 12b is disposed between the side wall surface of the stepped portion of the cylinder block cylindrical portion 2 and the stopper plate 15 via the flange portions of the bush 14 disposed on both sides in the axial direction. The movement in the axial direction is restricted by the side wall surface of the step portion and the stopper plate 15. The structure of the other part in the drive plate 12 is the same as that of the drive plate of Example 1 (12 in FIG. 2).

  The rack member 13 is fixed to the drive plate 12 at the outer periphery of the cylindrical portion 12 b of the drive plate 12. The structure of the other part in the rack member 13 is the same as that of the rack member of Example 1 (13 in FIG. 2).

  According to the second embodiment, the same effect as the first embodiment is obtained.

  An internal combustion engine starter according to Embodiment 3 of the present invention will be described with reference to the drawings. FIG. 6 is a plan view seen from the axial direction schematically showing the configuration of the internal combustion engine starter according to Embodiment 3 of the present invention. In FIG. 6, a flywheel (corresponding to 5 in FIG. 2) and a driven plate (corresponding to 19 in FIG. 2) are omitted.

  The third embodiment is a modification of the first embodiment. The number of the groove portions 13a of the rack member 13 is increased (nine in FIG. 6), and the phase between the position of the hooking surface 13b of the groove portion 13a and the position of the claw member 17 is changed. It is a staggered one. That is, the two claw members 17 are set so as not to be hooked with the hooking surface 13b at the same time, one claw member 17 is hooked with the hooking surface 13b, and the other claw member 17 is not hooked with the hooking surface 13b. Other configurations are the same as those of the first embodiment.

  According to the third embodiment, the same effects as those of the first embodiment are obtained, and the idling angle until the claw member 17 is hooked with the hooking surface 13b is reduced, so that the responsiveness is improved.

  A starter for an internal combustion engine according to Embodiment 4 of the present invention will be described with reference to the drawings. FIG. 7: is the top view seen from the axial direction which showed typically the structure of the starter of the internal combustion engine which concerns on Example 4 of this invention. In FIG. 7, the flywheel (corresponding to 5 in FIG. 2) and the driven plate (corresponding to 19 in FIG. 2) are omitted.

  The fourth embodiment is a modification of the first embodiment, and is set so that the contact point between the claw member 17 and the hooking surface 13b of the rack member 13 is arranged on the same line as the load direction generated when the engine is started. It is. That is, the direction of the load generated at the time of starting the engine is the circle 13c passing through the contact point between the claw member 17 and the hooking surface 13b (the rotation axis of the crankshaft 3 is determined) when the crankshaft 3 is rotated clockwise in FIG. This corresponds to the direction of the tangent line 17a. The tangent line 17a passes through the contact point between the claw member 17 and the hooking surface 13b and the rotation axis of the claw member 17 (the central axis of the pin member 18). The shape of the groove 13a and the hooking surface 13b of the rack member 13 and the shape of the tip of the claw member 17 are set so as to satisfy the above conditions. Other configurations are the same as those of the first embodiment.

  According to the fourth embodiment, the same effects as those of the first embodiment can be obtained, and since the generation of moment load in the claw member 17 is suppressed, the strength of the claw member 17 can be ensured.

  An internal combustion engine starter according to Embodiment 5 of the present invention will be described with reference to the drawings. FIG. 8: is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 5 of this invention. In FIG. 8, the flywheel (corresponding to 5 in FIG. 2) and the driven plate (corresponding to 19 in FIG. 2) are omitted.

  The fifth embodiment is a modification of the first embodiment, and the front end of the claw member 17 contacts the cylindrical portion 12 a of the drive plate 12 when the front end of the claw member 17 is rotated radially outward by centrifugal force. In order to avoid this, a stopper portion 17b is provided in the claw member 17, and a stopper portion 19a is provided in a driven plate (corresponding to 19 in FIG. 2). The stopper portion 17 b is a portion protruding in the direction opposite to the direction extending from the end portion (a portion around the pin member 18) of the claw member 17 to the tip portion, and rotates with the rotation of the claw member 17. The stopper portion 19a is a portion protruding from the plate surface of the driven plate (corresponding to 19 in FIG. 2) (the portion cut and bent in FIG. 8), and when the tip of the claw member 17 rotates radially outward. The stopper portion 17b is locked so that the tip of the claw member 17 does not contact the cylindrical portion 12a of the drive plate 12. Other configurations are the same as those of the first embodiment.

  According to the fifth embodiment, the same effects as those of the first embodiment can be obtained, and excessive rotation of the claw member 17 can be suppressed. Therefore, a required space can be reduced and a reliable angle setting of the claw member 17 can be performed.

  An internal combustion engine starter according to Embodiment 6 of the present invention will be described with reference to the drawings. FIG. 9 is a plan view seen from the axial direction schematically showing the configuration of the claw member in the starting device for the internal combustion engine according to the sixth embodiment of the present invention.

  The sixth embodiment is a modification of the first embodiment, and the surface of a portion (a tip portion or a radially inner portion) of the claw member 17 that can come into contact with other members (particularly, the rack member 13 shown in FIG. 1). Is provided with a buffer portion 17c made of a buffer material such as rubber. Other configurations are the same as those of the first embodiment. Instead of providing the buffer member 17c on the claw member 17, a buffer member made of a buffer material such as rubber may be provided on the surface of the rack member (corresponding to 13 in FIG. 1) that can come into contact with the claw member 17. .

  According to the sixth embodiment, the same effects as those of the first embodiment can be obtained, and the shock when the rack member (corresponding to 13 in FIG. 1) and the claw member 17 come into contact with each other can be absorbed by the buffer portion 17c. Is hooked to the rack member (corresponding to 13 in FIG. 1), and when the tip of the claw member 17 springs down to the rack member (corresponding to 13 in FIG. 1) by a spring (corresponding to 20 in FIG. 1). The sound of hitting can be reduced.

  An internal combustion engine starter according to Embodiment 7 of the present invention will be described with reference to the drawings. FIG. 10: is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 7 of this invention. FIG. 11 is a cross-sectional view taken along the line XX ′ in FIG. 10 schematically showing the configuration of the starting device for the internal combustion engine according to the seventh embodiment of the present invention. In FIG. 10, the flywheel 5 and the driven plate 19 in FIG. 11 are omitted.

  The seventh embodiment is a modification of the first embodiment, and not only the pin member 18 that rotatably supports the claw member 17 is fixed to the driven plate 19 but also the pin member 18 on the opposite side of the driven plate 19 side. The end is fixed to the support plate 24. The support plate 24 is fixed to the driven plate 19 by rivets 25. The claw member 17 is disposed between the driven plate 19 and the support plate 24. Other configurations are the same as those of the first embodiment.

  According to the seventh embodiment, the same effect as that of the first embodiment can be obtained, and the strength of the pin member 18 that receives power transmission from the claw member 17 can be achieved by using both the driven member 19 and the support plate 24 for the pin member 18. It is possible to reinforce.

  An internal combustion engine starter according to Embodiment 8 of the present invention will be described with reference to the drawings. FIG. 12: is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 8 of this invention. FIG. 13 is a partial cross-sectional view taken along the line XX ′ of FIG. 12 schematically showing the configuration of the starting device for the internal combustion engine according to the eighth embodiment of the present invention. FIG. 14 is a partial cross-sectional view taken along the line YY ′ of FIG. 12 schematically showing the configuration of the starting device for the internal combustion engine according to the eighth embodiment of the present invention. In FIG. 12, the flywheel (corresponding to 5 in FIG. 2) and the driven plate 19 are omitted.

  The eighth embodiment is a modification of the first embodiment, and does not fix the rack member 13 and the drive plate 12, but allows the rack member 13 and the drive plate 12 to rotate relative to each other so that the rack member 13 and the drive plate 12 can be rotated. A damper 30 is provided for buffering (absorbing) a fluctuating torque generated between the rack member 13 and the drive plate 12 when torsion occurs between them. In the damper 30, a plurality of accommodating portions 13 d are formed in the rack member 13, and the support member 31, the rivet 32, the buffer material 33, and the cover plate 34 are included. The configuration excluding the damper 30 is the same as that of the first embodiment.

  The rack member 13 is disposed between the drive plate 12 and the cover plate 34, and regulates the axial movement of the assembly of the drive plate 12, the support member 31 and the cover plate 34 connected by the rivet 32. The rack member 13 also serves as a bearing that rotatably supports the drive plate 12. The rack member 13 has a plurality of accommodating portions 13d formed so as to penetrate through portions between adjacent groove portions 13a.

  The accommodating portion 13 d is a space that accommodates the support member 31 and the buffer material 33. There are eight accommodating portions 13d in the rack member 13 in the configuration of FIG. In each accommodating portion 13d, a supporting member 31 and a buffer material 33 are accommodated in series in the circumferential direction. In the accommodating portion 13d, one end surface in the circumferential direction can contact and separate from the support member 31, and the other end surface in the circumferential direction is in contact with the cushioning material 33.

  The support member 31 is a block-like member that supports one end of the cushioning material 33. The support member 31 is accommodated in the accommodating portion 13 d of the rack member 13 and is disposed between the drive plate 12 and the cover plate 34. The support member 31 is connected to the drive plate 12 and the cover plate 34 by rivets 32 and rotates integrally with the drive plate 12 and the cover plate 34. The support member 31 has an end surface on one side in the circumferential direction that can contact and separate from an end surface on one side in the circumferential direction of the accommodating portion 13 d, and an end surface on the other side in the circumferential direction is in contact with the cushioning material 33.

  The rivet 32 is a member for connecting and fixing the support member 31 to the drive plate 12 and the cover plate 34. One end of the rivet 32 is caulked to the drive plate 12, and the other end is caulked to the cover plate 34, and an intermediate portion is inserted through a through-hole in the support member 31.

  The cushioning member 33 is a member that cushions the fluctuating torque generated between the rack member 13 and the drive plate 12 when torsion occurs between the rack member 13 and the drive plate 12. For the buffer material 33, for example, rubber, a coil spring or the like can be used. The buffer material 33 is accommodated in the accommodating portion 13 d of the rack member 13 and is disposed between the drive plate 12 and the cover plate 34. The cushioning material 33 is arranged between the end surface in the circumferential direction of the accommodating portion 13 d and the support member 31. The buffer material 33 has one end in the circumferential direction in contact with the end surface in the circumferential direction of the accommodating portion 13 d and the other end in the circumferential direction is in contact with the support member 31 connected to the drive plate 12 by the rivet 32. When the claw member 17 abuts on the hooking surface 13b of the rack member 13 and the torsion occurs between the rack member 13 and the drive plate 12, the cushioning material 33 is moved toward the support member 31 by the end surface in the circumferential direction of the accommodating portion 13d. It is pressed and compressed, thereby buffering the fluctuation torque generated between the rack member 13 and the drive plate 12.

  The cover plate 34 is a plate-like member that covers the housing portion 13 d of the rack member 13. The cover plate 34 is disposed on the opposite side of the rack member 13 to the drive plate 12 side. In the cover plate 34, the drive plate 12 and the support member 31 are connected by a plurality of rivets 32. The cover plate 34 serves as a stopper that prevents the cushioning material 33 from falling out of the housing portion 13 d of the rack member 13.

  According to the eighth embodiment, the same effects as those of the first embodiment can be obtained, and the shock when the claw member 17 is hooked on the rack member 13 by the damper 30 can be absorbed, and the claw member 17 is hooked on the rack member 13. The sound of hitting can be reduced.

  An internal combustion engine starter according to Embodiment 9 of the present invention will be described with reference to the drawings. FIG. 15: is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 9 of this invention. In FIG. 15, the flywheel (corresponding to 5 in FIG. 2) and the driven plate (corresponding to 19 in FIG. 2) are omitted.

  The ninth embodiment is a modification of the eighth embodiment. In the rack member 13, a curved surface 13e is formed from the groove 13a to the hooking surface 13b. The curved surface 13e is formed so that, when the engine is started, the tip of the claw member 17 that is in contact with the groove 13a approaches the hooking surface 13b so that the tip of the claw member 17 is smoothly hooked on the hooking surface 13b. It is. When the tip of the claw member 17 slides on the curved surface 13e, the tip of the claw member 17 moves slightly outward in the radial direction. Other configurations are the same as those in the eighth embodiment.

  According to the ninth embodiment, the same effect as that of the eighth embodiment is obtained, and the tip of the claw member 17 slides on the curved surface 13e from the groove portion 13a and is smoothly hooked on the hooking surface 13b, thereby burdening the damper 30. Can be relaxed.

  An internal combustion engine starter according to Embodiment 10 of the present invention will be described with reference to the drawings. FIG. 16 is a cross-sectional view schematically showing the configuration of the internal combustion engine starter according to Embodiment 10 of the present invention. FIG. 17 is a plan view seen from an arrow A in FIG. 16 schematically showing the configuration of the driven plate in the internal combustion engine starter according to Embodiment 10 of the present invention. FIG. 18 is a plan view seen from an arrow A in FIG. 16 schematically showing the configuration of the side plate in the internal combustion engine starter according to Embodiment 10 of the present invention. FIG. 19 is a plan view seen from an arrow A in FIG. 16 schematically showing the configuration of the center plate in the internal combustion engine starter according to Embodiment 10 of the present invention. FIG. 16 is a cross-sectional view corresponding to the line XX ′ in FIG.

  The tenth embodiment is a modification of the first embodiment, and does not fix the pin member 18 and the driven plate 41 (corresponding to the driven plate 19 of FIG. The damper 40 is capable of moving in the direction, and cushions (absorbs) the fluctuating torque generated between the pin member 18 and the driven plate 41 when the pin member 18 is moved (twisted) in the circumferential direction with respect to the driven plate 41. Is provided. The damper 40 includes a driven plate 41, a side plate 42, a center plate 43, a sheet member 44, a coil spring 45, and a pin member 46. Moreover, instead of using a spring (20 in FIG. 2), a spring stopper fitting (21 in FIG. 2), and a pin member (22 in FIG. 2) as means for urging the tip of the claw member 17 radially inward. Only the spring 47 is used. The configuration excluding the damper 40 and the spring 47 is the same as that of the first embodiment.

  The driven plate 41 is an annular plate that can be rotationally driven by the drive plate 12 via the rack member 13, the claw member 17, the pin member 18, the center plate 43, the sheet member 44, the coil spring 45, and the sheet member 44 ( (Refer FIG. 16, FIG. 17). The driven plate 41 has a hole 41 e for inserting the bolt 4. The driven plate 41 is fixed to the crankshaft 3 together with the flywheel 5 by bolts 4 and rotates integrally with the crankshaft 3 and the flywheel 5. The driven plate 41 extends radially outward from the rack member 13. The driven plate 41 has a plurality of (six in FIG. 17) hole portions 41d for caulking one end of the pin member 46 at the outer peripheral portion. The driven plate 41 is connected to the side plate 42 at a predetermined interval by a pin member 46 at the outer peripheral portion. The driven plate 41 rotates integrally with the side plate 42. The driven plate 41 includes a plurality of (four in FIG. 17) window portions for accommodating the pair of sheet members 44 and the coil springs 45 in the damper 40 at a position shifted in the circumferential direction from the portion connected by the pin member 46. 41a. The window portion 41a can be brought into contact with and separated from the pair of sheet members 44 at both end surfaces in the circumferential direction, and comes into contact with both the pair of sheet members 44 when the damper 40 is not twisted. When the damper 40 is twisted in a state where the member 17 is not pressed, the pair of sheet members 44 are in contact with each other. When the rack member 13 presses the claw member 17, the pair is twisted in the damper 40. This is in contact with one of the sheet members 44. The driven plate 41 has a convex portion 41 b slidably in contact with the center plate 43 at a portion radially outside the damper 40. The driven plate 41 is slidably in contact with the convex portion 43 b of the center plate 43 at a portion radially inward of the damper 40. The driven plate 41 has a notch 41 c for preventing contact with the pin member 18.

  The side plate 42 is an arc-shaped plate member (see FIGS. 16 and 18). There are two side plates 42. The side plate 42 has a hole 42 d for caulking the other end of the pin member 46. The side plate 42 is connected to the driven plate 41 by a pin member 46 at a predetermined interval. The side plate 42 rotates integrally with the driven plate 41. The side plate 42 includes a plurality (for each side plate 42 in FIG. 18) for accommodating the pair of sheet members 44 and the coil spring 45 in the damper 40 at a position shifted in the circumferential direction from the portion connected by the pin member 46. 2) window portions 42a. The window portion 42a can be brought into contact with and separated from the pair of sheet members 44 at the end surfaces on both sides in the circumferential direction. When the damper 40 is not twisted, the window portion 42a is in contact with both of the pair of sheet members 44, and the rack member 13 is clawed. When the damper 40 is twisted in a state where the member 17 is not pressed, the pair of sheet members 44 are in contact with each other. When the rack member 13 presses the claw member 17, the pair is twisted in the damper 40. This is in contact with one of the sheet members 44. The side plate 42 has a convex portion 42 b slidably in contact with the center plate 43 at a portion radially outside the damper 40. The side plate 42 has a convex portion 42 c that is slidably in contact with the center plate 43 at a portion radially inward of the damper 40. The side plate 42 is divided into two parts so as not to conflict with the pin member 18.

  The center plate 43 is an annular plate member (see FIGS. 16 and 19). The center plate 43 has one end of a plurality of (two in FIG. 19) pin members 18 fixed to the outer peripheral portion, and supports the claw member 17 via the pin member 18 so as to be swingable. The center plate 43 has a plurality of (four in FIG. 19) window portions 43 a for accommodating the pair of sheet members 44 and the coil spring 45. The window 43a is formed in a cutout shape. The window portion 43a can be brought into contact with and separated from one sheet member 44 at one end surface in the circumferential direction, and always comes into contact with one sheet member 44 regardless of the twist of the damper 40. A predetermined pin member 46 is inserted through the window 43a at a position where it does not come into contact with the damper 40. The center plate 43 has a convex portion 43 b that is slidably in contact with the driven plate 41 at a portion radially inward of the damper 40. The center plate 43 has a plurality (two in FIG. 19) of stopper portions 43c for restricting excessive twisting of the damper 40. The stopper portion 43c is formed in a notch shape. Another predetermined pin member 46 is inserted through the stopper portion 43c. The stopper portion 43c restricts excessive twisting of the damper 40 by the other predetermined pin member 46 coming into contact with the end surfaces on both sides in the circumferential direction. Movement of the center plate 43 in the radial direction is restricted by the plurality of window portions 43 a by the sheet members 44 accommodated in the window portions 41 a and 42 a of the driven plate 41 and the side plate 42.

  The sheet member 44 is a component part of the damper 40, and is accommodated in the window portions 41a, 42a, and 43a formed in the driven plate 41, the side plate 42, and the center plate 43, and the periphery of the window portions 41a, 42a, and 43a. It is arranged between the end face in the direction and the end of the coil spring 45. Resin can be used for the sheet member 44 in order to reduce wear of the coil spring 45.

  The coil spring 45 is a component of the damper 40, and is housed in windows 41a, 42a, 43a formed in the driven plate 41, the side plate 42, and the center plate 43, and a pair of sheet members disposed at both ends. 44. The coil spring 45 contracts when a twist occurs between the driven plate 41 and the side plate 42 and the center plate 43 while the rack member 13 presses the claw member 17, and the driven plate 41 and the side plate 42 and the center plate 43 contract. The shock due to the rotation difference from the plate 43 is absorbed.

  The pin member 46 is a member for connecting and fixing the driven plate 41 and the side plate 42 at a predetermined interval. The pin member 46 is inserted through the window 43 a and the stopper 43 c of the center plate 43. The pin member 46 regulates excessive twisting of the damper 40 by abutting against end faces on both sides in the circumferential direction of the stopper portion 43c.

  The spring 47 is an elastic member that biases the tip of the claw member 17 so as to rotate radially inward. The spring 47 is arranged around the portion of the pin member 18 between the center plate 43 and the claw member 17. One end of the spring 47 is supported or fixed to the center plate 43 and the other end biases the claw member 17 so that the tip of the claw member 17 is rotated to the inner peripheral side.

  According to the tenth embodiment, the same effects as in the first embodiment can be obtained, and the shock when the claw member 17 is hooked on the rack member 13 by the damper 40 can be absorbed, and the claw member 17 is hooked on the rack member 13. The sound of hitting can be reduced.

  An internal combustion engine starter according to Embodiment 11 of the present invention will be described with reference to the drawings. FIG. 20 is a cross-sectional view schematically showing the configuration of the claw member in the internal combustion engine starter according to Embodiment 11 of the present invention. FIG. 20 is a cross section in the circumferential direction.

  The eleventh embodiment is a modification of the first embodiment, and a shock when the tip portion of the claw member 50 (corresponding to 17 in FIG. 1) can be expanded and contracted and the tip portion is hooked on the hooking surface 13 b of the rack member 13. This is provided with a damper function for absorbing water. The claw member 50 is a claw-like member that can be engaged with a hooking surface (corresponding to 13b in FIG. 1) of a rack member (corresponding to 13 in FIG. 1), and is a constituent member of the hooking mechanism. The claw member 50 is disposed radially outside the rack member (corresponding to 13 in FIG. 1), and overlaps the rack member (corresponding to 13 in FIG. 1). The claw member 50 includes a tip member 51, a terminal member 52, and an elastic member 53. Other configurations are the same as those of the first embodiment.

  The tip member 51 is a member that is hooked on a hooking surface (corresponding to 13b in FIG. 1) of a rack member (corresponding to 13 in FIG. 1) when it is bounced down radially inward. The tip member 51 is slidably supported by the end member 52. The tip member 51 has an extending portion 51 a that extends into the accommodating portion 52 a of the end member 52. The extending portion 51 a includes a stopper portion 51 b that is locked by the stopper portion 52 b of the end member 52 in order to prevent the tip member 51 from falling off the end member 52. The tip member 51 is in contact with one end of the elastic member 53 in the housing portion 52 a of the end member 52.

  The end member 52 is a member swingably attached to a pin member (18 in FIG. 2) fixed to a driven plate (corresponding to 19 in FIG. 2). The end member 52 has a hole 52c for attaching to a pin member (corresponding to 18 in FIG. 2). The end member 52 can swing around a pin member (corresponding to 18 in FIG. 2) as a rotation axis. The end member 52 is biased by a spring (corresponding to 20 in FIG. 1) so that the tip member 51 rotates inward in the radial direction. In the end member 52, when the driven plate (corresponding to 19 in FIG. 2) is rotating, the distal end member 51 jumps outward in the radial direction because the centrifugal force applied to the end member 51 overcomes the urging force of the spring 20. increase. The end member 52 slidably supports the tip member 51 and has an accommodating portion 52 a for accommodating the elastic member 53. The end member 52 is in contact with the other end of the elastic member 53 in the accommodating portion 52a. The end member 52 has a stopper portion 52 b that locks the stopper portion 51 b of the tip member 51 in order to prevent the tip member 51 from falling off the end member 52.

  The elastic member 53 is a member that cushions a shock applied to the claw member 50 when the tip member 51 is hooked on a hooking surface (corresponding to 13b in FIG. 1) of the rack member (corresponding to 13 in FIG. 1). For the elastic member 53, for example, rubber, a coil spring or the like can be used. The elastic member 53 is accommodated in the accommodating portion 52 a of the end member 52 and is disposed between the tip member 51 and the end member 52. The elastic member 53 is compressed when the tip member 51 contacts the hooking surface (corresponding to 13b in FIG. 1) of the rack member (corresponding to 13b in FIG. 1) and the tip member 51 contracts to the end member 52 side. Shock is shocked when the tip member 51 hits the hooking surface (corresponding to 13b in FIG. 1).

  According to the eleventh embodiment, the same effects as those of the first embodiment are obtained, and the shock when the tip member 51 is hooked on the rack member (corresponding to 13 in FIG. 1) by the elastic member 53 in the claw member 50 is absorbed. It is possible to alleviate the sound of hitting when the claw member 51 is caught by the rack member (corresponding to 13 in FIG. 1).

  An internal combustion engine starter according to Embodiment 12 of the present invention will be described with reference to the drawings. FIG. 21 is a cross-sectional view schematically showing the configuration of the internal combustion engine starter according to Embodiment 12 of the present invention. FIG. 21 is a cross-section corresponding to the section XX ′ in FIG.

  The twelfth embodiment is a modification of the second embodiment and uses a ball bearing 60 as a means for bearing the drive plate 12 on the cylinder block cylindrical portion 2 instead of using a bush (14 in FIG. 5). The ball bearing 60 has a plurality of balls interposed between an inner ring and an outer ring. The inner ring is fixed to the cylinder block cylindrical portion 2, and movement in the axial direction is restricted by the side wall surface of the stepped portion of the cylinder block cylindrical portion 2 and the stopper plate 15. A cylindrical portion 12b of the drive plate 12 is fixed to the outer ring. The rack member 13 may be fixed to the outer ring instead of the cylindrical portion 12b of the drive plate 12. Other configurations are the same as those of the second embodiment.

  According to the twelfth embodiment, the same effects as those of the second embodiment can be obtained, and by using the ball bearing 60, it is possible to cope with a higher rotation and a higher load.

  An internal combustion engine starter according to Embodiment 13 of the present invention will be described with reference to the drawings. FIG. 22: is the top view seen from the axial direction which showed typically the structure of the starting device of the internal combustion engine which concerns on Example 13 of this invention. FIG. 23 is a cross-sectional view taken along the line XX ′ in FIG. 22 schematically showing the configuration of the starting device for the internal combustion engine according to the thirteenth embodiment of the present invention. FIG. 24 is a plan view seen from the axial direction for explaining the operation after the start cancellation of the starting device for the internal combustion engine according to the thirteenth embodiment of the present invention. FIG. 25: is the top view seen from the axial direction which showed typically the structure of the claw member in the starting device of the internal combustion engine which concerns on Example 13 of this invention, and sectional drawing between YY 'in a top view. is there. In FIG. 22, the flywheel 5 and the driven plate 19 in FIG. 23 are omitted.

  The thirteenth embodiment is a modification of the first embodiment, and includes ring members 70 and 71 as means for assisting the jumping of the tip of the claw member 17 after the start is released. Other configurations are the same as those of the first embodiment.

  The ring member 70 is a ring-shaped member disposed around the pin member 18. The ring member 70 is fixed to the end portion of the claw member 17 and rotates integrally with the claw member 17. The ring member 70 is frictionally engaged with the ring member 71 at the corners of the outer peripheral surface, and rotates in the direction opposite to the rotation of the ring member 71 according to the rotation of the ring member 71. The ring member 70 has a tapered notch 70a that does not frictionally engage with the ring member 71 at a part of the corner of the outer peripheral surface (see FIG. 25). The notch 70a is set so as not to contact the ring member 71 toward the ring member 71 when the tip of the claw member 17 jumps up radially outward.

  The ring member 71 is a ring-shaped member that is fixed to the drive plate 12 at the outer periphery of the rack member 13. The ring member 71 rotates integrally with the drive plate 12. The ring member 71 has a surface that can come into contact with a corner portion of the ring member 70 excluding the notch portion 70a. When the rotational speed of the drive plate 12 becomes lower than the rotational speed of the driven plate 19, the ring member 71 rotates counterclockwise with respect to the driven plate 19 in FIG. 22. At this time, the ring member 71 acts to rotate the ring member 70 clockwise in FIG. 22 by the frictional force so as to jump the tip end portion of the claw member 17 radially outward. Since the notch 70a of the ring member 70 faces the rotating shaft side of the crankshaft 3 when the tip end portion of the claw member 17 jumps outward in the radial direction, the ring member 71 faces the ring member 70 with respect to the ring member 70. The power that attempts to jump the tip end radially outward is not transmitted (see FIG. 24).

  According to the thirteenth embodiment, the same effects as those of the first embodiment can be obtained, and the ring members 70 and 71 can be used to create a chance to jump up the tip of the claw member 17, thereby The hook can be released smoothly.

  An internal combustion engine starter according to Embodiment 14 of the present invention will be described with reference to the drawings. FIG. 26: is the top view seen from the axial direction which showed typically the structure of the starter of the internal combustion engine which concerns on Example 14 of this invention. FIG. 27 is a cross-sectional view taken along the line XX ′ of FIG. 26 schematically showing the configuration of the starting device for the internal combustion engine according to the fourteenth embodiment of the present invention. In FIG. 26, the flywheel 5 and the driven plate 19 in FIG. 27 are omitted.

  The fourteenth embodiment is a modification of the thirteenth embodiment, and instead of using ring members (70 and 71 in FIG. 22) as means for assisting the jumping of the tip of the claw member 17 after the start is released, the drive plate 12, the outer periphery of the surface to which the rack member 13 is attached is defined as a contact portion 12 c, and the claw member 17 can slide on the contact portion 12 c within a predetermined angle range in a state where the tip portion of the claw member 17 is bounced down. It is intended to touch. Referring to FIG. 26, a region where the claw member 17 and the contact portion 12 c overlap when viewed from the axial direction becomes the sliding portion 17 e of the claw member 17. The sliding part 17e is a flat surface. There is a gap between the claw member 17 and the driven plate 19, and a ring-shaped wave spring 72 disposed around the pin member 18 is arranged in the gap. The wave spring 72 biases the claw member 17 toward the drive plate 12. When the tip part jumps up, the claw member 17 is completely separated from the contact part 12c. Other configurations are the same as those in the thirteenth embodiment.

  According to the fourteenth embodiment, the same effects as the thirteenth embodiment can be obtained, and the cost can be reduced by reducing the number of parts.

  An internal combustion engine starter according to Embodiment 15 of the present invention will be described with reference to the drawings. FIG. 28 is a plan view seen from the axial direction schematically showing the configuration of the starter for the internal combustion engine according to the fifteenth embodiment of the present invention. FIG. 29 is a cross-sectional view taken along the line XX ′ in FIG. 28 schematically showing the configuration of the starting device for the internal combustion engine according to the fifteenth embodiment of the present invention. In FIG. 28, the flywheel 5 and the driven plate 19 in FIG. 29 are omitted.

  The fifteenth embodiment is a modification of the thirteenth embodiment, and instead of using ring members (70 and 71 in FIG. 22) as means for assisting the jumping of the tip of the claw member 17 after the start is released, the drive plate 12 is provided with an annular ring member 71 so that the claw member 17 is slidably in contact with the ring member 71 in a range of a predetermined angle in a state where the tip of the claw member 17 is bounced down. Referring to FIG. 28, the region where the claw member 17 and the ring member 71 overlap when viewed from the axial direction becomes the sliding portion 17 e of the claw member 17. The sliding part 17e is a flat surface. The ring member 71 is disposed so as to be concentric with the rotational axis of the drive plate 12 when viewed from the axial direction. Other configurations are the same as those in the thirteenth embodiment.

  According to the fifteenth embodiment, the same effects as the thirteenth embodiment can be obtained, and the cost can be reduced by reducing the number of parts.

  It should be noted that the embodiments and examples can be changed and adjusted within the scope of the entire disclosure (including claims) of the present invention and based on the basic technical concept. Various combinations and selections of various disclosed elements are possible within the scope of the claims of the present invention. That is, the present invention of course includes various variations and modifications that could be made by those skilled in the art according to the entire disclosure including the claims and the technical idea.

DESCRIPTION OF SYMBOLS 1 Starter 2 Cylinder block cylindrical part 3 Crankshaft 3a Rotating shaft 4 Bolt 5 Flywheel 6 Pinion gear 11 Ring gear 12 Drive plate 12a Cylindrical part 12b Cylindrical part 12c Abutting part 13 Rack member (non-engaging member)
13a Groove 13b Hook surface (engaged surface)
13c Circle 13d Housing 13e Curved surface 14 Bush 15 Stopper plate 16 Bolt 17 Claw member (engaging member)
17a Tangent line 17b Stopper part 17c Buffer part 17d Hole part 17e Sliding part 18 Pin member 19 Driven plate 19a Stopper part 20 Spring (biasing member)
21 Spring stopper bracket 22 Pin member 24 Support plate 25 Rivet 30 Damper 31 Support member 32 Rivet 33 Buffer material 34 Cover plate 40 Damper 41 Driven plate 41a Window portion 41b Protruding portion 41c Notch portion 41d Hole portion 41e Hole portion 42 Side plate 42a Window Part 42b convex part 42c convex part 42d hole part 43 center plate 43a window part 43b convex part 43c stopper part 44 sheet member 45 coil spring (elastic member)
46 Pin member 47 Spring 50 Claw member 51 Tip member 51a Extension part 51b Stopper part 52 End member 52a Storage part 52b Stopper part 52c Hole part 53 Elastic member 60 Ball bearing 70 Ring member 70a Notch part 71 Ring member (other ring members) )
72 Wave Spring

Claims (25)

A pinion gear mounted on the output shaft of the starter,
A ring gear meshing with the pinion gear;
A drive plate that rotates integrally with the ring gear;
A driven plate that rotates integrally with the crankshaft of the internal combustion engine;
At least one engaging member pivotably attached to the driven plate;
The engagement is performed when the drive plate is attached to the drive plate, arranged closer to the rotation axis of the drive plate than the engagement member, and the rotation speed of the drive plate is higher than the rotation speed of the driven plate. An engaged member that engages with the tip of the member;
With
When the rotational speed of the driven plate becomes higher than the rotational speed of the drive plate, the distal end portion of the engaging member is disengaged from the engaged member, and the rotational axis of the drive plate is caused by centrifugal force. A starter for an internal combustion engine, wherein the starter is rotated away from the engine. Comprising at least one urging member for urging the distal end portion of the engagement member so as to approach the rotation axis of the drive plate;
When the rotational speed of the driven plate is higher than the rotational speed of the drive plate, the engagement member is disengaged from the distal end portion of the engagement member, and the distal end portion of the engagement member 2. The starter for an internal combustion engine according to claim 1, wherein when the centrifugal force exceeds the urging force of the urging member, the engine is rotated away from the rotation axis of the drive plate.   The engaged member is formed in a substantially annular shape, and a plurality of groove portions recessed at predetermined intervals are formed on the outer peripheral surface of the engaged member, and one of the circumferential surfaces of each groove portion is formed. The starter for an internal combustion engine according to claim 1 or 2, further comprising an engaged surface that engages with a distal end portion of the engaging member.   4. The starter for an internal combustion engine according to claim 3, wherein the groove is a curved surface and is smoothly connected to the engaged surface. The engagement member has two or more,
When at least one of the plurality of engaging members is engaged with one of the corresponding plurality of engaged surfaces, the other engaging members are not engaged with the engaged surface. The starter for an internal combustion engine according to claim 3 or 4, characterized by the above.   A contact point between the engagement member and the non-engagement surface when engaged with the engagement member and the engaged surface is arranged on the same line as a load direction generated when the internal combustion engine is started. The starter for an internal combustion engine according to any one of claims 3 to 5, wherein: The direction of load generated when the internal combustion engine is started is a direction of a tangent line of a circle passing through a contact point between the engaging member and the engaged surface,
The internal combustion engine starter according to claim 6, wherein the tangent line passes through a contact point between the engaging member and the engaged surface and a rotation shaft of the engaging member. The engaging member has a stopper portion,
2. The driven plate has another stopper portion that locks the stopper portion when the distal end portion of the engagement member rotates away from the rotation axis of the drive plate. The starter for an internal combustion engine according to any one of 7. Comprising at least one support plate attached to the driven plate;
The engagement member is disposed between the driven plate and the support plate, and is swingably attached to the driven plate and the support plate. An internal combustion engine starter according to claim 1.   The starter for an internal combustion engine according to any one of claims 1 to 9, wherein the engaging member includes a buffer portion made of a buffer material on a surface of a portion that can come into contact with the engaged member.   The starter for an internal combustion engine according to any one of claims 1 to 9, wherein the engaged member has a buffer portion made of a buffer material on a surface of a portion that can come into contact with the engagement member. The engaged member is rotatably attached to the drive plate,
The starter for an internal combustion engine according to any one of claims 1 to 11, further comprising a damper that cushions torsion between the drive plate and the engaged member. The damper is
An accommodating portion formed in the engaged member;
A support member fixed to the drive plate and inserted into the housing;
A cushioning material disposed between an end face in the circumferential direction of the housing portion and the support member;
The starter for an internal combustion engine according to claim 12, comprising: The engagement member is attached to the driven plate so as to be rotatable in the same direction as the rotation direction of the driven plate,
The starter for an internal combustion engine according to any one of claims 1 to 11, further comprising a damper that cushions torsion between the engagement member and the driven plate. The damper is
A center plate rotatably supported by the driven plate, and wherein the engagement member is swingably attached;
An elastic member that cushions torsion between the center plate and the driven plate;
The starter for an internal combustion engine according to claim 14, comprising:   12. The engagement member according to claim 1, further comprising a damper that absorbs shock when the distal end portion is engaged with the engaged member, while the distal end portion is extendable and contractable. A starter for an internal combustion engine according to one. The engaging member is
An end member attached to the driven plate in a swingable manner and having an accommodating portion;
A tip member slidably attached to the end member and engageable with the engaged member;
An elastic member housed in the housing portion and disposed between the tip member and the end member in the sliding direction of the tip member;
The starter for an internal combustion engine according to claim 16, comprising:   18. The internal combustion engine start-up according to claim 1, wherein one end is fixed to the driven plate, and the other end includes a pin member that supports the engaging member in a swingable manner. apparatus. The internal combustion engine has a cylindrical portion that extends in the axial direction at a portion farther from the rotational axis of the drive plate than the crankshaft on the outer surface,
The internal combustion engine starter according to any one of claims 1 to 18, wherein one of the drive plate and the engaged member is rotatably supported by the cylindrical portion.   The starter for an internal combustion engine according to claim 19, further comprising a bush attached to the cylindrical portion and bearings one of the drive plate and the engaged member.   The starter for an internal combustion engine according to claim 19, further comprising a ball bearing attached to the cylindrical portion and bearings one of the drive plate and the engaged member. A ring member arranged concentrically with the rotation shaft of the engagement member and rotating integrally with the engagement member;
Another ring member that is arranged concentrically with the rotational axis of the drive plate and rotates integrally with the drive plate;
With
The ring member is frictionally engaged with the other ring member at a corner of the outer peripheral surface;
When the rotational speed of the driven plate is higher than the rotational speed of the drive plate, the distal end portion of the engagement member is separated from the rotational axis of the drive plate by the frictional force between the ring member and the other ring member. The starter for an internal combustion engine according to any one of claims 1 to 21, wherein the starter is maintained at a position separated by a predetermined distance.   The ring member has a notch portion that avoids contact between the ring member and the other ring member when the internal combustion engine is started at a part of the corner portion of the outer peripheral surface. Item 23. The internal combustion engine starter according to Item 22. The drive plate has a contact portion that can contact the engagement member;
The engaging member has a sliding portion that can slide with the contact portion of the drive plate,
When the rotational speed of the driven plate is higher than the rotational speed of the drive plate, the distal end portion of the engagement member has a rotational axis of the drive plate due to a frictional force generated between the sliding portion and the contact portion. The starter for an internal combustion engine according to any one of claims 1 to 21, wherein the starter is maintained at a position away from a predetermined distance from the engine. A ring member arranged concentrically with the rotation shaft of the drive plate and rotating integrally with the engagement member;
The engaging member has a sliding portion that can slide with the ring member,
When the rotational speed of the driven plate is higher than the rotational speed of the drive plate, the distal end portion of the engaging member is separated from the rotational axis of the drive plate by a frictional force generated between the sliding portion and the ring member. The starter for an internal combustion engine according to any one of claims 1 to 21, wherein the starter is maintained at a position separated by a predetermined distance.

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