JP4831035B2 - Starter - Google Patents

Description

  The present invention relates to a starter provided with an impact absorbing device.

As a prior art, a starter described in Patent Document 1 is known.
As shown in FIG. 4, the starter includes an output shaft 100 that is driven and rotated by a motor (not shown), a pinion gear 120 that is fitted to the outer periphery of the output shaft 100 via a bearing 110, and the output shaft 100. And an impact absorbing device 130 provided between the pinion gear 120 and the pinion gear 120. The shock absorbing device 130 includes a first case 140 that is serrated and fitted to the outer periphery of the output shaft 100, a second case 150 that is serrated and fitted to the outer periphery of a cylindrical portion provided integrally with the pinion gear 120, and both cases. The intermediate case 160 is disposed between the cases 140 and 150, and the rubber damper 170 is sandwiched between the cases 140 to 160. For example, an impact from the engine side (the ring gear on the engine side is The rubber damper 170 has a function of reducing the impact value while delaying the transmission of the impact when the rubber damper 170 is compressed and deformed in the circumferential direction when the pinion gear 120 is hit.
JP 2006-207573 A

By the way, when the impact absorbing device 130 receives an impact, the rubber damper 170 is pressed and compressed in the circumferential direction, and then restored by an elastic force. Since the rubber damper 170 repeats compression and restoration, friction is generated between the rubber damper 170 and each of the cases 140, 150, and 160. In order to reduce the friction, lubricating grease is applied to the contact surfaces of the two. Has been.
However, when the inside of the engine case where the starter pinion gear 120 and the ring gear on the engine side are not sealed, a large amount of muddy water, dust, etc. from the outside due to the flooding of the vehicle, etc. There is a risk of entering the inside (the portion where the rubber damper 170 inside the case is disposed).

  In particular, the shock absorbing device 130 shown in FIG. 4 has gaps between the first case 140 and the intermediate case 160 and between the intermediate case 160 and the second case 150. The oil content of the grease is absorbed by the muddy water and dust that have entered the inside of the shock absorber 130 from these gaps. In addition, the oil component may be scattered by centrifugal force and flow out to the outside. As a result, the coefficient of friction between the rubber damper 170 and each of the cases 140, 150, 160 increases, and the surface of the rubber damper 170 is peeled off, cracks, etc. occur at an early stage, resulting in a reduction in shock absorbing performance. Is expected.

Further, when other oil such as engine oil or LLC (antifreeze) enters, there is a risk of swelling and property change of the rubber damper 170, so there is a concern about problems due to changes over time.
The present invention has been made on the basis of the above circumstances. The purpose of the present invention is to prevent the intrusion of muddy water, dust, oil, etc. from the outside into the shock absorber used in the starter. It is to stabilize the absorption performance.

(Invention of Claim 1)
The starter of the present invention includes an output shaft that is driven by a motor to rotate, a pinion gear that is supported by the output shaft and transmits a driving torque generated by the motor to an engine ring gear, and the driving torque of the motor is transmitted through the output shaft. A shock absorber provided in a torque transmission path that is transmitted to the pinion gear, wherein the shock absorber is arranged between a plurality of cases that are axially opposed to each other and rotatably arranged. When a shock is applied to the torque transmission path, the plurality of cases rotate relative to each other and the elastic body compresses and deforms in the circumferential direction, thereby delaying the transmission of the shock. has a function of reducing the impact value, and, between the case adjacent to each other in the axial direction is a seal member is mounted to close an axial gap formed outer periphery in the radial direction, this The outer periphery of the case where the sealing member is mounted, wherein the projections to prevent the sealing member jumps out toward the outside in the radial direction is provided.

According to said structure, since the clearance gap which arises between each case is blocked | closed with the sealing member, foreign materials, such as muddy water, dust, and engine oil, are outside the shock absorber (especially the elastic body is arrange | positioned). Intrusion into the inside of the case can be prevented. As a result, the oil component of the grease is not absorbed by dust and the like, and the grease component can be prevented from being scattered due to centrifugal force. The friction coefficient can be stabilized without increasing rapidly. As a result, damage to the elastic body can be suppressed, and shock absorption performance can be stabilized.
In addition, since a protrusion is provided on the outer periphery of the case where the seal member is mounted to prevent the seal member from jumping outward in the radial direction, when the centrifugal force acts on the seal member, the protrusion of the case The sealing member can be prevented from protruding outward in the radial direction by the portion, and the sealing performance can be maintained.

(Invention of Claim 2)
The starter according to claim 1, wherein both the elastic body and the seal member are made of rubber, and the rubber hardness of the seal member is equal to or less than the rubber hardness of the elastic body.
Since the impact absorbing device of the present invention has a seal member mounted in a gap between adjacent cases in the axial direction, if the rubber hardness of the seal member is larger than the rubber hardness of the elastic body, the impact absorbing performance of the elastic body will be improved. Produces an impact. That is, the amount of bending of the elastic body when subjected to an impact is reduced, in other words, the same result as when the spring constant of the elastic body is increased is produced.
Therefore, the shock absorbing performance of the elastic body can be ensured by setting the rubber hardness of the sealing member to be equal to or lower than the rubber hardness of the elastic body.

(Invention of Claim 3 )
3. The starter according to claim 1, wherein the elastic body is disposed in a state where movement in a radial direction is restricted with respect to the case, and the seal member has a gap between the elastic body and the outer peripheral surface in the radial direction. In this state, it is mounted between cases adjacent in the axial direction.
In this case, since the seal member does not contact the elastic body, the seal member does not affect the movement (compression and restoration) of the elastic body, and a stable shock absorbing performance can be ensured.

(Invention of Claim 4 )
The starter according to claim 1 or 2, wherein the plurality of cases include an input side case disposed on the input side of the torque transmission path, an output side case disposed on the output side of the torque transmission path, and the two cases. The intermediate case is made of resin, and the protrusions are provided integrally with the intermediate case.
When the protrusion is provided on the resin intermediate case, the protrusion can be easily formed by molding with a mold, and the shape of the protrusion can be easily changed.

(Invention of Claim 5 )
The starter according to claim 1 or 2, wherein the plurality of cases are disposed between the two cases so that the first case that engages with the output shaft, the second case that engages with the pinion gear, and the two cases. The intermediate case is made of resin, and the protrusions are integrally provided.
When the protrusion is provided on the resin intermediate case, the protrusion can be easily formed by molding with a mold, and the shape of the protrusion can be easily changed.

(Invention of Claim 6 )
The starter according to any one of claims 1 to 5, wherein the pinion gear is always meshed with the ring gear.
When the starter pinion gear is always meshed with the ring gear on the engine side, not only the impact that occurs when the engine starts, that is, the impact that occurs when the ring gear hits the pinion gear due to engine rotation fluctuations during cranking, the engine rotates in reverse. When, for example, the reverse rotation due to the swing of the crankshaft that occurs when the engine is stopped, or when the vehicle reverses due to an engine stall on the climbing road, the reverse rotation impacts the pinion gear that is always meshed with the ring gear. As transmitted. For this reason, in a starter in which the pinion gear always meshes with the ring gear, the impact absorbing device has a large function to absorb the impact received from the engine side.

(Invention of Claim 7 )
The starter described in claim 6 is used in an engine automatic stop / restart system that automatically controls stop and restart of the engine.
An automatic engine stop / restart system (generally also called an idle stop system, an eco-run system, etc.), for example, automatically stops the engine when the vehicle stops temporarily at an intersection or traffic jam, and then starts a predetermined start by the driver. When the operation is performed, the engine is automatically restarted, which is effective for improving the fuel consumption of the vehicle or improving the exhaust emission. In a vehicle equipped with this automatic engine stop / restart system, the number of engine starts, that is, the number of starter starts inevitably increases compared to a vehicle not equipped with the system.

  By the way, when the engine is started (during cranking), noise unpleasant for the user (a tapping sound when the ring gear strikes the pinion gear) is generated along with the impact. For this reason, in a vehicle equipped with the above system, unpleasant noise and impact are generated each time the engine is restarted. On the other hand, the starter of the present invention can reduce the impact and unpleasant noise generated at the start of the engine by the impact absorbing device. There is an effect that can be reduced.

The best mode for carrying out the present invention will be described in detail with reference to the following examples. However, Example 1 shows a reference example to which the present invention is not applied, and Example 2 shows an example to which the present invention is applied.

FIG. 1 is a half sectional view of the impact absorbing device 10, and FIG. 2 is a half sectional view of the starter 1.
As shown in FIG. 2, the starter 1 according to the first embodiment is provided in a motor 2 that generates a rotational force in a built-in armature 3 and a motor circuit for energizing the armature 3 from a battery (not shown). An electromagnetic relay 4 that opens and closes a main contact (to be described later), an anti-reverse clutch 5 that prevents reverse rotation of the armature 3, a speed reducer 6 that decelerates rotation of the armature 3, and the speed reducer 6. The output shaft 7 to which the driving torque of the motor 2 is transmitted, the pinion gear 9 fitted to the outer periphery of the output shaft 7 via the bearing 8, and the impact absorbing device 10 provided between the output shaft 7 and the pinion gear 9 Etc. The starter 1 of this embodiment can be used in an engine automatic stop / restart system that automatically controls engine stop and restart.

The motor 2 is provided with a commutator 12 on one end side (right side in the drawing) of the armature shaft 11 that outputs the rotation of the armature 3, and the armature 3 is connected to the armature 3 via a brush 13 disposed on the outer periphery of the commutator 12. This is a known commutator motor that is energized, and a permanent magnet 15 (or a field coil) may be disposed on the inner periphery of a yoke 14 that forms a magnetic circuit. The armature shaft 11 has an end on one end protruding from the commutator 12 that is rotatably supported by the end frame 17 via a bearing 16, and an end on the non-commutator side (the other end) on the output shaft 7. It is inserted into the inner periphery of the cavity formed at the end of this through a bearing 18 (see FIG. 1) so as to be relatively rotatable.
The end frame 17 is fitted and assembled in an opening on the end side (right side in the drawing) of the yoke 14, and a plurality of through bolts (not shown) are fastened and fixed to the starter housing 19.

The electromagnetic relay 4 has a solenoid incorporating the electromagnetic coil 20 and the plunger 21, and a resin contact cover 22 fixed to the solenoid, and a main contact is disposed inside the contact cover 22.
The solenoid has a known function of forming an electromagnet by energizing the electromagnetic coil 20 to attract the plunger 21 and closing the main contact in conjunction with the movement of the plunger 21. When the energization of the electromagnetic coil 20 is stopped and the attraction force of the electromagnet disappears, the plunger 21 is pushed back in the left direction by the reaction force stored in the return spring 23 (see FIG. 2) to open the main contact. Manipulate.

  The main contact is a B fixed contact 25 connected to the high potential side (battery side) of the motor circuit via the B terminal bolt 24 and a low potential side (motor 2 side) of the motor circuit via the M terminal bolt 26. The M fixed contact 27 to be connected and the movable contact 28 which is movable integrally with the plunger 21 and intermittently connects between the two fixed contacts 25, 27 are formed. The main contact is closed when the fixed contacts 25 and 27 are connected to each other, and the main contact is disconnected when the movable contact 28 is separated from the fixed contacts 25 and 27 and the connection between the fixed contacts 25 and 27 is interrupted. Open state.

  Each of the B terminal bolt 24 and the M terminal bolt 26 is fixed to the contact cover 22, and a battery cable (not shown) is connected to the distal end side of the B terminal bolt 24 protruding in the axial direction (right direction in the drawing) from the contact cover 22. Similarly, the terminal of the motor lead wire 29 is connected to the tip end side of the M terminal bolt 26 protruding in the axial direction from the contact cover 22. Note that the opposite terminal side of the motor lead wire 29 is drawn into the motor 2 through a grommet 30 sandwiched between the yoke 14 and the end frame 17 of the motor 2 and connected to the brush 13 on the positive electrode side. Yes.

The reverse rotation prevention clutch (hereinafter referred to as clutch 5) forms a plurality of cam chambers (not shown) between an inner 31 provided in a part of the armature shaft 11 and an outer peripheral surface of the inner 31. The outer 32 and the roller 33 disposed in the cam chamber are configured.
The outer 32 has an outer wall portion 32 a that extends outward in the radial direction, and an outer peripheral portion of the outer wall portion 32 a is positioned in the axial direction and is restricted from rotating with respect to the starter housing 19. The cam chamber is formed in a wedge shape in which the space for housing the roller 33 is gradually narrowed in the counter-rotating direction of the armature shaft 11.

The roller 33 is urged by a spring (not shown) in a narrowing direction (a counter-rotating direction of the armature shaft 11) in which the space of the cam chamber is narrowed, and has a function of intermittently transmitting torque between the inner 31 and the outer 32. .
When the reverse rotation occurs in the engine and the reverse rotation is transmitted to the armature shaft 11 via the speed reducer 6, the clutch 5 moves the roller 33 in the narrowing direction of the cam chamber, and the inner 31 and the outer The armature shaft 11 is prevented from rotating reversely by being locked between the armature shaft 32 and the armature shaft 11.
On the other hand, when the engine is driven by the starter 1, the roller 33 moves in the cam chamber anti-narrow direction (direction in which the space becomes wider), which is the rotation direction of the armature shaft 11, and idles. Allow rotation of

The speed reducer 6 is a planetary gear speed reducer that can be decelerated on the same axis as the armature shaft 11, and is rotationally restricted via a sun gear 34 formed on the countercommutator side of the armature shaft 11 and a torque limiter described below. The internal gear 35 and a plurality of planetary gears 36 (see FIG. 1) meshing with both gears 34 and 35, and the revolving motion of the planetary gear 36 is transmitted to the output shaft 7.
As shown in FIG. 1, the torque limiter has a rotating disk 39 whose rotation is restricted by a frictional force between a center case 37 and a fixed disk 38, and an excessive torque exceeding the sliding torque of the rotating disk 39 causes internal teeth. When applied to the gear 35, the rotating disk 39 slides (rotates) against the frictional force, allowing the internal gear 35 to rotate and interrupting transmission of excessive torque.

The center case 37 is disposed inside the starter housing 19 at right angles to the output shaft 7, abuts against a step provided on the inner periphery of the starter housing 19, is positioned in the axial direction, and rotates with respect to the starter housing 19. It is regulated.
As shown in FIG. 2, the output shaft 7 is disposed on the same axis as the armature shaft 11, and the end on the side opposite to the motor is rotatably supported by the tip of the starter housing 19 via a bearing 40. The end of the motor 2 is connected to the speed reducer 6 and is rotatably supported by the center case 37 via a bearing 41 (see FIG. 1).
The pinion gear 9 is always meshed with a ring gear 42 (see FIG. 2) on the engine side, and is connected to the output shaft 7 via an impact absorbing device 10 described below.

Next, the impact absorbing device 10 will be described with reference to FIG.
The shock absorber 10 includes a ring drive 43 that forms an input side case or a first case, a ring drive 44 that forms an output side case or a second case, a ring space 45 that forms an intermediate case, a ring A plurality of rubber dampers 46 assembled between the drive 43 and the ring space 45, and between the ring space 45 and the ring drive 44, and a seal member mounted between the cases adjacent in the axial direction. It is composed of a ring 47 and the like .

The ring drive 43 is provided with a cylindrical boss portion 43a at the radial center, and the boss portion 43a is serrated to the outer periphery of the output shaft 7 and is connected to the output shaft 7 so as not to be relatively rotatable. Yes.
As with the ring drive 43, the ring drive 44 is provided with a cylindrical boss portion 44a at the center in the radial direction, and this boss portion 44a is serrated on the outer periphery of the cylindrical portion 9a provided integrally with the pinion gear 9. In combination, the pinion gear 9 is connected to the pinion gear 9 so as not to rotate relative thereto.
The ring space 45 is rotatably fitted to the outer periphery of a boss portion 43 a provided in the ring drive 43 and is disposed between the ring drive 43 and the ring drive 44.

Between the ring drive 43 and the ring space 45 facing each other in the axial direction and between the ring space 45 and the ring drive 44, damper spaces (not shown) (for example, three locations) in the circumferential direction are respectively shown. A total of six rubber dampers 46 are stored in each damper space.
Further, inside the shock absorbing device 10, in order to suppress wear due to friction of the rubber damper 46, surface peeling, cracks, etc., the surface of the rubber damper 46, a ring drive 43 that contacts the rubber damper 46, a ring space 45, and Lubricating grease is applied to each surface of the ring drive 44. The ring drive 43 and the ring drive 44 are each made of metal (for example, iron) in order to ensure the strength necessary for torque transmission, and the ring space 45 is made of, for example, a resin that can contribute to weight reduction. is there.

The ring drive 43 and the ring space 45 adjacent to each other in the axial direction, and the ring space 45 and the ring drive 44 are respectively arranged with a predetermined interval in the axial direction in a state where the rubber damper 46 is incorporated therebetween. . That is, when an impact is transmitted from the engine side and the rubber damper 46 is bent (compressed and deformed) in the circumferential direction, the ring drive 43 and the ring space 45, and the ring space 45 and the ring drive 44 do not frictionally contact each other. In addition, a predetermined gap is secured in the axial direction.
Further, a rubber O-ring 47 is formed between the ring drive 43 and the ring space 45 and between the ring space 45 and the ring drive 44 in order to close an axial gap generated on the outer periphery in the radial direction. Is installed. However, the rubber hardness of the O-ring 47 is set to be equal to or lower than the hardness of the rubber damper 46. As an example, the rubber hardness of the O-ring 47 is Hs60 ± 10, and the hardness of the rubber damper 46 is Hs80 ± 5.

Next, the operation of the starter 1 will be described.
When the main contact of the motor circuit is closed by the electromagnetic relay 4, power is supplied from the battery to the armature 3 to generate a rotational force on the armature 3. The rotation of the armature 3 is decelerated by the speed reducer 6 and transmitted to the output shaft 7, and further transmitted from the output shaft 7 to the pinion gear 9 via the shock absorber 10, and the rotation of the pinion gear 9 is transmitted to the ring gear 42. And crank the engine.
When the engine completes explosion and the engine speed exceeds the starter speed, for example, a one-way clutch (not shown) built in the ring gear 42 idles and torque is generated between the crankshaft of the engine and the ring gear 42. Therefore, the rotation of the engine is not transmitted to the pinion gear 9, and overrun of the armature 3 can be prevented.

  Further, when the engine rotates reversely, for example, when the engine rotates backward when the vehicle moves backward due to the crankshaft swinging generated when the engine stops, or when the vehicle moves backward due to an engine on a climbing road, the ring gear 42 The one-way clutch built in is engaged. Therefore, in the starter 1 in which the pinion gear 9 is always meshed with the ring gear 42, the reverse rotation of the engine is transmitted from the ring gear 42 to the pinion gear 9. On the other hand, since the starter 1 of the present embodiment includes the reverse rotation preventing clutch 5 that can prevent the reverse rotation of the armature 3, even if the reverse rotation of the engine is input to the starter 1, Reverse rotation can be prevented.

In the above operation, the impact absorbing device 10 is used when the starter 1 receives an impact from the engine side (for example, when the ring gear 42 strikes the pinion gear 9 during cranking, or when the engine rotates in the reverse direction). The impact is generated while the transmission of the impact is delayed by the rubber damper 46 being bent (compressed and deformed) in the circumferential direction while the ring drive 43 and the ring drive 44 are rotated relative to each other via the ring space 45. Has the function of reducing
The torque limiter rotates when an excessive impact that cannot be absorbed by the impact absorbing device 10, that is, an excessive impact that exceeds the torque limiter set torque (sliding torque of the rotating disk 39) is transmitted to the output shaft 7. When the disk 39 slides against the frictional force, it has a function of interrupting transmission of impact force. Thereby, an excessive impact is not applied to the torque transmission path of the starter 1, and damage due to the impact received from the engine side can be avoided.

(Effect of Example 1)
The shock absorber 10 used in the starter 1 of the present embodiment has an O-ring 47 in an axial gap formed between the ring drive 43 and the ring space 45 and between the ring space 45 and the ring drive 44. It is installed. Thereby, it is possible to prevent foreign matters such as muddy water, dust, and engine oil from entering the inside of the impact absorbing device 10 (particularly, the portion where the rubber damper 46 is disposed) from the outside. As a result, the oil component of the grease is not absorbed by dust or the like, and the grease component can be prevented from being scattered by centrifugal force, so that the surface of the rubber damper 46 can be kept in good lubrication, and the rubber damper can be maintained. Since the coefficient of friction between 46 and the ring drive 43 and the ring drive 44 can be stabilized, damage to the rubber damper 46 (for example, peeling of the surface of the rubber damper 46, cracking, etc.) can be prevented.
In addition, since the O-ring 47 has a lower rubber hardness than the rubber damper 46, it hardly affects the movement (compression and restoration) of the rubber damper 46 when receiving an impact from the engine side, and ensures a stable shock absorbing performance. it can.

FIG. 3 is an enlarged cross-sectional view of the seal portion of the impact absorbing device 10.
The impact absorbing device 10 according to the second embodiment is an example in which protrusions 45a are provided on both sides in the axial direction of the outer peripheral wall of the ring space 45, as shown in FIG. The protrusion 45a protrudes in an inclined state toward the O-ring 47 so that the outer periphery of the O-ring 47 on the ring space 45 side can be held. Or you may provide in the shape curved along the outer periphery shape of the O-ring 47. FIG. As a result, the O-ring 47 is not only sandwiched in the axial direction between the ring drive 43 and the ring space 45 and between the ring space 45 and the ring drive 44, but also the outer periphery of the O-ring 47 by the protrusion 45a. Since a part is held, it is possible to prevent the O-ring 47 from projecting or jumping out from the gap by centrifugal force.
Moreover, since the ring space 45 provided with the protrusion 45a is made of resin, the protrusion 45a can be easily formed by molding with a mold, and the shape of the protrusion 45a can be easily changed. However, the ring drive 43 and the ring drive 44 that are made of metal can be provided with protrusions.

  Further, the O-ring 47 of this embodiment does not come into contact with the rubber damper 46, and a gap C is secured between the inner periphery (inner diameter) of the O-ring 47 and the outer peripheral surface of the rubber damper 46, as shown in FIG. Has been. That is, since the rubber damper 46 is disposed in a state where movement in the radial direction is restricted with respect to the ring space 45, the O-ring 47 having an inner diameter sufficient to ensure a gap C between the rubber damper 46 and the outer peripheral surface of the rubber damper 46. used. Even when the O-ring 47 is compressed at the maximum, that is, when the O-ring 47 is compressed in the axial direction and the inner periphery of the O-ring 47 is pushed out toward the rubber damper 46, the O-ring 47 is pressed against the rubber damper 46. It is desirable to ensure the clearance C so that C ≧ 0 even when the O-ring 47 is compressed to the maximum. Thereby, since the O-ring 47 hardly contacts the rubber damper 46, the O-ring 47 does not affect the movement (compression and restoration) of the rubber damper 46 when an impact is transmitted from the engine side. Shock absorption performance can be secured.

(Modification)
In the impact absorbing device 10 described in the first embodiment, the rubber damper 46 is used as an elastic body . However, an elastic body other than the rubber damper 46 (for example, a torsion coil spring, an elastic resin material, or the like) can also be used.
In the impact absorbing device 10 described in the first and second embodiments, the rubber dampers 46 are arranged in series in two stages (a total of six) via the ring space 45 between the ring drive 43 and the ring drive 44. However, the number of the ring spaces 45 may be increased and the rubber dampers 46 may be arranged in three or more stages in series. Alternatively, the ring space 45 may be eliminated, and the rubber damper 46 may be disposed between the ring drive 43 and the ring drive 44. In this case, it goes without saying that an O-ring 47 is mounted as a seal member in the axial gap between the ring drive 43 and the ring drive 44.
In the first embodiment, the impact absorbing device 10 is provided between the output shaft 7 and the pinion gear 9, but is not limited to this position, and the torque transmission path of the starter 1 (the driving torque of the motor 2 is It suffices if it is on a route that is transmitted to the pinion gear 9 via the output shaft 7.

(Example 1) which is a half sectional view of an impact absorbing device. (Example 1) which is sectional drawing of a starter. (Example 2) which was expanded sectional drawing of the seal | sticker site | part of an impact-absorbing device. It is a half sectional view of an impact absorbing device showing the prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Starter 2 Motor 7 Output shaft 9 Pinion gear 10 Shock absorber 39 Rotating disk 42 Ring gear 43 Ring drive (input side case, first case)
44 Ring drive (output side case, second case)
45 Ring space (intermediate case)
45a Projection 46 Rubber damper (elastic body)
47 O-ring (seal member)
Clearance between CO ring and rubber damper

Claims (7)

An output shaft that rotates by being driven by a motor;
A pinion gear that is supported by the output shaft and transmits a driving torque generated by the motor to an engine ring gear;
A shock absorber provided in a torque transmission path through which the driving torque of the motor is transmitted to the pinion gear via the output shaft,
The impact absorbing device includes a plurality of cases that are axially opposed to each other and rotatably arranged with each other, and a plurality of elastic bodies that are arranged between the cases, and an impact is applied to the torque transmission path. The plurality of cases rotate relative to each other and the elastic body compresses and deforms in the circumferential direction, thereby reducing the impact value while delaying the transmission of the impact, and adjacent to the axial direction. Between the cases, a seal member that closes the gap in the axial direction generated on the outer periphery in the radial direction is mounted ,
A starter characterized in that a protrusion is provided on an outer peripheral portion of the case to which the seal member is mounted to prevent the seal member from jumping outward in the radial direction . The starter according to claim 1,
The elastic body and the seal member are both made of rubber, and the rubber hardness of the seal member is less than or equal to the rubber hardness of the elastic body. The starter according to claim 1 or 2,
The elastic body is disposed in a state in which radial movement is restricted with respect to the case,
The starter , wherein the seal member is mounted between the cases adjacent to each other in the axial direction with a gap between the seal member and a radially outer peripheral surface of the elastic body . The starter according to claim 1 or 2 ,
The plurality of cases are disposed so as to be relatively rotatable between an input side case disposed on the input side of the torque transmission path, an output side case disposed on the output side of the torque transmission path, and both cases. The starter has one or more intermediate cases, the intermediate cases are made of resin, and the protrusions are integrally provided . The starter according to claim 1 or 2 ,
The plurality of cases include a first case that engages with the output shaft, a second case that engages with the pinion gear, and one or more intermediate cases that are arranged to be relatively rotatable between the two cases. The starter is characterized in that the intermediate case is made of resin, and the protrusions are integrally provided. In any starter according to claims 1-5 ,
The starter characterized in that the pinion gear is always meshed with the ring gear . The starter according to claim 6 , wherein
A starter used for an engine automatic stop / restart system for automatically controlling stop and restart of the engine .

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