Patent Publication Number: US-2004051319-A1

Title: Starter

Description:
BACKGROUND OF THE INVENTION  
       [0001] This invention relates to a starter having a cantilever structure in which a pinion gear is attached on a distal end of a pinion shaft shiftably coupled around an output shaft of the starter.  
       [0002]FIG. 5 shows a conventional starter  100  having a cantilever structure, for example, disclosed in the Japanese Patent Application Laid-open No. 62-131972(1987) or in the Japanese Patent Publication No. 6-47982(1994).  
       [0003] The starter  100  includes a motor  110 , a rotary output shaft  120  driven by the motor  110 , a cylindrical pinion shaft  160  supported by a housing  140  via a ball bearing  130  and coupled around the output shaft  120  via a plain bearing  150 , a pinion gear  170  attached to a distal end (i.e., the left end in the drawing) of the pinion shaft  160  and supported in a cantilever fashion, and a one-way clutch  180  engaged with the output shaft  120  via a helical spline coupling so as to be shiftable on the output shaft  120  together with the pinion shaft  160  in an axial direction.  
       [0004] However, according to the above-described starter  100  characterized by the arrangement of the pinion gear  170  attached to the distal end of the pinion shaft  160 , due to its cantilever structure, a unbalanced load (high load) is imparted on the pinion gear  170  when the pinion gear  170  is brought into engagement with a ring gear  190  of the engine to start the engine. A large bending moment acts on the pinion shaft  160 . The plain bearing  150 , disposed between the pinion shaft  160  and the output shaft  120 , is provided with a tiny clearance against the output shaft  120  to reduce sliding resistance. Due to this clearance, the pinion shaft  160  inclines with respect to the output shaft  120  when it is driven. As a result, a significant twist is caused between the pinion shaft  160  and the output shaft  120 . This results in driving loss. The motor output is reduced, accordingly.  
       SUMMARY OF THE INVENTION  
       [0005] In view of the above-described problems, the present invention has an object to provide a starter capable of suppressing inclination of a pinion shaft when it is driven and also capable of reducing a twisting movement caused between the pinion shaft and an output shaft.  
       [0006] In order to accomplish the above and other related objects, the present invention provides a first starter including a motor generating a rotational force from its armature and a rotary output shaft driven by the motor. Two or more rolling-contact bearings, each having rolling members, are aligned in an axial direction. A pinion shaft is inserted in an inner cylindrical bore of each rolling-contact bearing so as to be supported by a housing via the rolling-contact bearings. The pinion shaft is disposed rotatably on the output shaft via a plain bearing. And, the pinion shaft is shiftable on the output shaft in the axial direction. A pinion gear is attached in a cantilever fashion to a distal end of the pinion shaft opposed to the motor. The pinion gear selectively meshes with a ring gear of an engine in a startup operation to transmit the rotational force of the motor to the ring gear.  
       [0007] According to this arrangement, the pinion shaft can be stably supported by a plurality of rolling-contact bearings aligned extensively in the axial direction. Even if an unbalanced load acts on the pinion gear when the pinion gear meshes with the ring gear to drive the ring gear, it is possible to prevent the pinion shaft from inclining. As a result, no twist is caused between the pinion shaft and the output shaft. It becomes possible to reduce the driving loss. The output reduction of the motor can be minimized.  
       [0008] Furthermore, aligning a plurality of rolling-contact bearings in the axial direction is effective in increasing the contact surface of the bearings contacting to the pinion shaft and to the housing. Heat transmitted from the inside of the motor to the pinion shaft can be effectively transmitted or released to the housing via the plurality of bearings. As a result, it becomes possible to reduce the inner temperature of the motor. The temperature of each rolling-contact bearing can be reduced, too. Thermal damage of the motor can be reduced. The lifetime of each bearing can be extended.  
       [0009] Furthermore, providing an axially extended contact surface between the rolling-contact bearings and the pinion shaft is effective to prevent water components or dusts from entering inside the housing of the starter.  
       [0010] Furthermore, supporting the pinion shaft by the plurality of rolling-contact bearings is advantageous in reducing a load imparted on individual bearing. As a result, it becomes possible to reduce the outer diameter of each bearing. The housing nose portion can be downsized in the radial direction and can be easily installed in a crowded engine room of an automotive vehicle.  
       [0011] Preferably, the rolling-contact bearings include a first rolling-contact bearing and a second rolling-contact bearing arranged next to each other in the axial direction with a predetermined clearance therebetween.  
       [0012] In this case, the space between the first and second rolling-contact bearings can be utilized as an oil reservoir. More specifically, when the pinion shaft shifts in the axial direction, excessive oil adhering on the surface of the pinion shaft is forcibly pushed or squeezed toward the rolling-contact bearings and is stored in this oil reservoir. Sliding performance of the pinion shaft is adequately kept for a long time.  
       [0013] Furthermore, the oil stored in the oil reservoir between the first and second bearings forms a long-lasting oil film spreading in the clearance between each rolling-contact bearing and the pinion shaft. The oil film reduces the sliding resistance of the pinion shaft and prevents water components or dusts from entering inside the housing.  
       [0014] Preferably, each of the rolling-contact bearings is a ball bearing having balls serving as rolling members.  
       [0015] Preferably, each of the rolling-contact bearings has rollers or needles serving as rolling members.  
       [0016] Furthermore, the present invention provides a second starter including a motor generating a rotational force from its armature and a rotary output shaft driven by the motor. The second starter includes a ball bearing having two or more rows of balls which are aligned in an axial direction and interposed between a pair of external and internal rings. A pinion shaft is inserted in an inner cylindrical bore of the ball bearing so as to be supported by a housing via the ball bearing. The pinion shaft is disposed rotatably on the output shaft via a plain bearing. And, the pinion shaft is shiftable on the output shaft in the axial direction. A pinion gear is attached in a cantilever fashion to a distal end of the pinion shaft opposed to the motor. The pinion gear selectively meshes with a ring gear of an engine in a startup operation to transmit the rotational force of the motor to the ring gear.  
       [0017] According to this arrangement, the axial length of the ball bearing becomes wide. Thus, the pinion shaft can be stably supported by the wide ball bearing. Even if an unbalanced load acts on the pinion gear when the pinion gear meshes with the ring gear to drive the ring gear, it is possible to prevent the pinion shaft from inclining. As a result, no twist is caused between the pinion shaft and the output shaft. It becomes possible to reduce the driving loss. The output reduction of the motor can be minimized.  
       [0018] Furthermore, using the ball bearing wide in the axial direction is effective in increasing the contact surface of the bearing contacting to the pinion shaft and to the housing. Heat transmitted from the inside of the motor to the pinion shaft can be effectively transmitted or released to the housing via the wide bearing. As a result, it becomes possible to reduce the inner temperature of the motor. The temperature of each ball bearing can be reduced, too. Thermal damage of the motor can be reduced. The lifetime of each bearing can be extended.  
       [0019] Furthermore, providing an axially extended contact surface between the ball bearing and the pinion shaft is effective to prevent water components or dusts from entering inside the housing of the starter.  
       [0020] Furthermore, supporting the pinion shaft by the plurality rows of balls of the ball bearing is advantageous in reducing a load imparted on individual rows of the balls. As a result, it becomes possible to reduce the outer diameter of the bearing. The housing nose portion can be downsized in the radial direction and can be easily installed in a crowded engine room of an automotive vehicle.  
       [0021] Preferably, the first or second starter further includes a one-way clutch coupled around the output shaft via a helical spline coupling and shiftable on the output shaft in the axial direction together with the pinion shaft to transmit rotation of the output shaft to the pinion shaft. An axial end of the rolling-contact (e.g., ball) bearing closer to the motor is disposed closely to the one-way clutch when the pinion shaft is positioned far from the motor to engage the pinion gear to the ring gear.  
       [0022] In general, lubrication oil is stored inside the one-way clutch. The lubrication oil, when heated, may come out of the one-way clutch. According to the above-described arrangement, the oil coming out of the one-way clutch reaches the rolling-contact bearing via the pinion shaft and lubricates the rolling-contact bearing. The lifetime of each rolling-contact bearing can be extended.  
       [0023] Preferably, the first or second starter further includes a one-way clutch coupled around the output shaft via a helical spline coupling and shiftable on the output shaft in the axial direction together with the pinion shaft to transmit rotation of the output shaft to the pinion shaft. A coupling clearance of the helical spline coupling is larger than a clearance between the rolling-contact (e.g., ball) bearing and the pinion shaft.  
       [0024] According to the conventional starter, it was necessary to employ an accurate helical spline (i.e., having a small coupling clearance) between the one-way clutch and the output shaft to prevent the pinion shaft from inclining. On the contrary, according to the present invention, inclining movement of the pinion shaft can be effectively prevented by the rolling-contact (e.g., ball) bearing. Thus, it becomes possible to increase the coupling clearance of the helical spline. As a result, it becomes possible to lower the required machining accuracy of the helical splines. The machining costs can be suppressed.  
       [0025] Preferably, in the first or second starter, a clearance between the plain bearing and the output shaft is larger than a clearance between the rolling-contact (e.g., ball) bearing and the pinion shaft.  
       [0026] According to this arrangement, even if the pinion shaft inclines with respect to the rolling-contact bearing by the maximum amount equivalent to the above clearance, no twist is caused between the inclined pinion shaft and the output shaft. Thus, the pinion shaft rotates smoothly. As a result, it becomes possible to reduce the driving loss. The output reduction of the motor can be minimized.  
       [0027] Preferably, in the first or second starter, a speed reduction device is disposed between the armature and the output shaft to reduce rotation of the armature and transmit reduced rotation to the output shaft.  
       [0028] In general, the starter having the speed reduction device produces a large torque and is subjected to a large unbalanced load applied on the pinion gear when the ring gear meshes with the pinion gear. Hence, the twist if caused due to inclination of the pinion shaft induces a large loss. Accordingly, the above-described arrangement for preventing the pinion shaft from inclining can be preferably employed for the starter equipped with the speed reduction device. Thus, the driving loss can be effectively reduced. 
     
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
     [0029] The above and other objects, features and advantages of the present invention will become more apparent from the following detailed description which is to be read in conjunction with the accompanying drawings, in which:  
     [0030]FIG. 1 is a partly cross-sectional view showing a non-operated condition of a starter in accordance with a first embodiment of the present invention;  
     [0031]FIG. 2 is a partly cross-sectional view showing an engine startup condition of the starter in accordance with the first embodiment of the present invention;  
     [0032]FIG. 3 is a partly cross-sectional view showing a starter in accordance with a second embodiment of the present invention;  
     [0033]FIG. 4 is a partly cross-sectional view showing a starter in accordance with a third embodiment of the present invention; and  
     [0034]FIG. 5 is a partly cross-sectional view showing a conventional starter.  
    
    
     DESCRIPTION OF THE PREFERRED EMBODIMENTS  
     [0035] Preferred embodiments of the present invention will be explained hereinafter with reference to attached drawings.  
     First Embodiment  
     [0036]FIG. 1 shows an overall arrangement of a starter  1  in accordance with a first embodiment of the present invention.  
     [0037] The starter  1  of the first embodiment includes a motor  2  generating a rotational force from its armature (not shown), an electromagnetic switch  3  which controls ON/OFF of electric current supplied to the motor  2 , a rotary output shaft  4  driven by the motor  2 , a pinion shaft  5  coupled around the output shaft  4  so as to be slidable in the axial direction, a pinion gear  6  attached to a distal end (i.e., an axial end far from the motor  2 ) of the pinion shaft  5 , and a one-way clutch  7  transmitting rotation of the output shaft  4  to the pinion shaft  5 .  
     [0038] The motor  2  is a well-known DC (i.e., direct-current) motor. When the electromagnetic switch  3  closes a motor contact (not shown), electric power is supplied from a vehicle battery (not shown) to the motor  2 . In response to the supplied electric power, the motor  2  generates magnetic field for rotating the armature.  
     [0039] The electromagnetic switch  3  includes a coil (not shown) which is supplied electric power in response to the turning-on operation of an IG (i.e., ignition) key. The electromagnetic switch  3  includes a plunger  8  which is disposed in a cylindrical bore of this coil and is slidable in the axial direction. When the coil is activated in response to supplied electric power, the plunger  8  is magnetically attracted to a predetermined direction (e.g., the right direction in the drawing). The plunger  8  shifts against a resilient force of a return spring (not shown) and closes the motor contact. The axial shift movement of the plunger  8  is transmitted to the one-way clutch  7  via a lever  9 . The one-way clutch  7  is thus pushed to a direction departing from the motor  2 .  
     [0040] The output shaft  4  is integrally provided with a rotary shaft (i.e., armature shaft) of the motor  2 . The output shaft  4  protrudes forward (i.e., leftward in FIG.  1 ) from a center plate  10 . The output shaft  4  is partly configured into an external helical spline  4   a . A stopper  11  is provided at the rear side of the external helical spline  4   a  (i.e., at one side closer to the motor  2 ). The stopper  11  regulates a stationary position of the one-way clutch  7 .  
     [0041] The center plate  10  closes a clutch opening (i.e., the left side opening) of a motor yoke  2   a , and also supports the output shaft  4  rotatably via the plain bearing  12 .  
     [0042] The pinion shaft  5  has a shaft portion  5   a  formed with a straight spline (not shown) at its front end. The pinion shaft  5  has a cylindrical sleeve portion formed continuously from the rear end of the shaft portion  5   a . A plain bearing  13  is press-fitted into an inner cylindrical bore of the cylindrical sleeve portion of the pinion shaft  5 . Thus, the pinion shaft  5  is coupled around an outer cylindrical surface of the output shaft  4  via the plain bearing  13 . On the other hand, an outer cylindrical surface of the pinion shaft  5  is supported by a housing  15  via a set of a plurality of (e.g., three in FIG. 1) rolling-contact bearings  14  aligned in the axial direction. A tiny clearance (hereinafter referred to as ‘CB’) is provided between the plain bearing  13  and the output shaft  4 .  
     [0043] The pinion gear  6  meshes with a ring gear  16  of an engine in a startup operation to transmit the rotational force of the motor  2  to the ring gear  16 . The pinion gear  6  is fixed to the shaft portion  5   a  of the pinion shaft  5  by spline coupling, and accordingly rotates together with the pinion shaft  5 .  
     [0044] The housing  15  has an installation surface  15   a  to be attached to the engine. The housing  15  has a nose portion  15   b  configured into a cylindrical shape and protruding from the installation surface  15   a  in the axial direction departing from the motor  2 .  
     [0045] Each rolling-contact bearing includes an outer race  14   a  and an inner race  14   b . The outer race  14   a  is press-fitted to an inner cylindrical wall of the nose portion  15   b . A tiny clearance (hereinafter referred to as ‘CA’) is provided between an inner race  14   b  and the pinion shaft  5 . The clearance ‘CA’ between the bearing  14  (i.e., inner race  14   b ) and the pinion shaft  5  is set to be smaller than the clearance ‘CB’ between the plain bearing  13  and the output shaft  4 .  
     [0046] The rightmost bearing  14  is disposed very closely to the one-way clutch  7  when the pinion shaft  5  is positioned far from the motor  2  to engage the pinion gear  6  to the ring gear  16 , as shown in FIG. 2.  
     [0047] The one-way clutch  7  is a roller type clutch preferably used for the starter  1 . The one-way clutch  7  consists of an outer member  7   a , an inner member  7   b , and a roller  7   c.    
     [0048] The outer member  7   a  is integrally formed with a cylindrical barrel portion which has an inner cylindrical surface on which an internal helical spline  7   d  is formed. The barrel portion couples around an outer cylindrical surface of the output shaft  4 . The internal helical spline  7   d  of the barrel portion meshes with the external helical spline  4   a  of the output shaft  4 . A coupling clearance (hereinafter referred to as ‘CC’) between the internal helical spline  7   d  and the external helical spline  7   a  is set to be larger than the clearance ‘CA’ between the bearing  14  and the pinion shaft  5 .  
     [0049] An end portion of the lever  9 , transmitting the axial shift movement of the plunger  8 , engages with an outer cylindrical portion of the barrel portion.  
     [0050] The inner member  7   b  is a cylindrical member integrally formed with the pinion shaft  5  and is disposed inside the outer member  7   a  in the radial direction.  
     [0051] The roller  7   c  is disposed in a wedged space defined between the outer member  7   a  and the inner member  7   b . When the outer member  7   a  rotates together with the output shaft  4 , the roller  7   c  is locked between the outer member  7   a  and the inner member  7   b . Thus, rotation of the outer member  7   a  is transmitted to the inner member  7   b  via the locked-up roller  7   c . When the rotational speed of the pinion shaft  5  exceeds the rotational speed of the output shaft  4 , the roller  7   c  is unlocked from the engagement with the outer member  7   a  and the inner member  7   b  and rotates freely. Hence, no driving force is transmitted between the outer member  7   a  and the inner member  7   b.    
     [0052] The starter  1  operates in the following manner.  
     [0053] In response to the turning-on operation of the IG key, the coil of electromagnetic switch  3  is energized to magnetically attract the plunger  8 . The movement of the plunger  8  shifting in the axial direction is transmitted to the one-way clutch  7  via the lever  9 . The one-way clutch  7  receives a pushing force from the lever  9  acting in the axial direction departing from the motor  2 . The one-way clutch  7  shifts forward (i.e., the axial direction departing from the motor  2 ) together with the pinion shaft  5 . The pinion gear  6  is then brought into contact with the ring gear  16  and is stopped.  
     [0054] Meanwhile, when the plunger  8  is positioned at a predetermined position where the motor contact is closed, electric power is supplied to the motor and accordingly the armature of the motor  2  rotates in response to the supplied electric power. The rotational force of the armature is transmitted to the output shaft  4 . Rotation of the output shaft  4  is then transmitted to the pinion shaft  5  via the one-way clutch  7 . When the pinion gear  6  rotates to an angular position engageable with the ring gear  16 , the pinion shaft  5  receives a thrust force caused between the helical splines  4   a  and  7   d  and is pushed forward. Accordingly, the pinion gear  6  meshes with the ring gear  16  (refer to FIG. 2). The rotational force of the motor  2  is transmitted to the ring gear  16  via the pinion gear  6  for cranking of the engine.  
     [0055] When the pinion gear  6  engages with the ring gear  16  to drive the ring gear  16 , the pinion gear  6  receives a load as a reaction force from the ring gear  16 . In this case, as the pinion shaft  5  supports the pinion gear  6  in a cantilever fashion, a bending moment acts on the pinion shaft  5 . This bending moment acts as a force inclining the pinion shaft  5 . However, the above-described first embodiment provides a plurality of rolling-contact bearings  14  aligned in the axial direction to support the pinion shaft  5 . This effectively prevents the pinion shaft  5  from inclining.  
     [0056] Furthermore, the clearance ‘CB’ between the plain bearing  13  and the output shaft  4  is larger than the clearance ‘CA’ between the bearing  14  and the pinion shaft  5 . Accordingly, even if the pinion shaft  5  inclines with respect to the bearing  14  by the maximum amount equivalent to the clearance ‘CA’, no twist is caused between the inclined pinion shaft  5  and the output shaft  4 . Thus, the pinion shaft  5  rotates smoothly. As a result, it becomes possible to reduce the driving loss. The output reduction of the motor  2  can be minimized.  
     [0057] Furthermore, aligning a plurality of rolling-contact bearings  14  in the axial direction is effective in increasing the contact surface of the bearings contacting to the pinion shaft  5  and to the housing  15 . Heat transmitted from the inside of motor  2  to the pinion shaft  5  can be effectively transmitted or released to the housing  15  via the plurality of bearings  14 . As a result, it becomes possible to reduce the inner temperature of the motor  2 . Thermal damage of the motor  2  can be reduced. The temperature of the bearings  14  can be lowered. The lifetime of each bearing  14  can be extended.  
     [0058] Furthermore, providing an axially extended contact surface between the plurality of bearings  14  and the pinion shaft  5  is effective to prevent water components or dusts from entering inside the housing  15  from the opening of the nose portion  15   b.    
     [0059] Furthermore, supporting the pinion shaft  5  by the plurality of bearings  14  is advantageous in reducing a load imparted on individual bearing  14 . As a result, it becomes possible to reduce the outer diameter of each bearing  14 . The housing nose portion  15   b  can be downsized in the radial direction and can be easily installed in a crowded engine room of an automotive vehicle.  
     [0060] Furthermore, the rightmost bearing  14  is disposed very closely to the one-way clutch  7  when the pinion shaft  5  is positioned far from the motor  2  to engage the pinion gear  6  to the ring gear  16 . This is advantageous in that oil component coming out of the one-way clutch  7  reaches the bearings  14  via the pinion shaft  5  and lubricates the bearings  14 . The lifetime of each bearing  14  can be extended.  
     [0061] According to the conventional starter, it was necessary to employ an accurate helical spline (i.e., having a small coupling clearance) between the one-way clutch and the output shaft to prevent the pinion shaft  5  from inclining. On the contrary, according to the above-described first embodiment of the present invention, inclining movement of the pinion shaft  5  can be effectively prevented by the plurality of rolling-contact bearings  14 . Thus, it becomes possible to increase the coupling clearance ‘CC’ between the internal helical spline  7   d  and the external helical spline  4   a . The coupling clearance ‘CC’ is set to be larger than the clearance ‘CA’ between the bearing  14  and the pinion shaft  5 . As a result, it becomes possible to lower the required machining accuracy of the helical splines  7   d  and  4   a . The machining costs can be suppressed.  
     Second Embodiment  
     [0062]FIG. 3 shows an overall arrangement of a starter  1   a  in accordance with a first embodiment of the present invention.  
     [0063] The starter  1   a  of the second embodiment, as shown in FIG. 3, has only one rolling-contact bearing  14 ′ supporting the pinion shaft  5 . According to the second embodiment, the rolling-contact bearing  14 ′ is a ball bearing including a plurality rows (e.g., two rows) of balls  14   c  disposed in the axial direction between the outer race  14   a  and the inner race  14   b . In other words, the axial length of the bearing  14 ′ (i.e., the axial length of the outer race  14   a  or inner race  14   b ) in the second embodiment is longer than that of each bearing  14  disclosed in the first embodiment.  
     [0064] According to the second embodiment, it becomes possible to obtain substantially the same effects as those of the first embodiment without providing a plurality of bearings.  
     [0065] The rest of the starter  1   a  according to the second embodiment is substantially the same as that of the starter  1  disclosed in the first embodiment.  
     Third Embodiment  
     [0066]FIG. 4 shows an overall arrangement of a starter  1   b  in accordance with a third embodiment of the present invention.  
     [0067] The starter  1   c  of the third embodiment, as shown in FIG. 4, has a first bearing  14 A and a second bearing  14 B (e.g., ball bearings) which are disposed next to each other and spaced from each other with a predetermined distance in the axial direction for supporting the pinion shaft  5 .  
     [0068] According to the arrangement of the third embodiment, in addition to the effect of the first embodiment, the axial space between the first bearing  14 A and the second bearing  14 B can be utilized as an oil reservoir. More specifically, when the pinion shaft  5  shifts in the axial direction, excessive oil adhering on the surface of the pinion shaft  5  is forcibly pushed or squeezed toward the bearings  14  and is stored in the oil reservoir between the first bearing  14 A and the second bearing  14 B. Sliding performance of the pinion shaft  5  is adequately kept for a long time.  
     [0069] Furthermore, the oil stored in the oil reservoir between the first bearing  14 A and the second bearing  14 B forms a long-lasting oil film spreading in the clearance between each bearing  14  and the pinion shaft  5 . The oil film reduces the sliding resistance of the pinion shaft  5  and prevents water components or dusts from entering inside the housing  15 .  
     [0070] Furthermore, the starter  1   b  of the third embodiment includes a speed reduction device  17  disposed between the armature and the output shaft  4 . Rotation of the armature is reduced by the speed reduction device  17  and is transmitted to the output shaft  4 .  
     [0071] The speed reduction device  17 , as shown in FIG. 4, is a planetary gear type speed reduction device which includes an armature shaft  2   b  coaxial with the output shaft  4 , a carrier  18  integral with the output shaft  4 , and a plurality of planetary gears  19  rotatably supported by the carrier  18 . Each planetary gear  19 , meshing with a sun gear  20  at a radially inner side and also meshing with an internal gear  21  at a radially outer side, causes an orbital motion about the sun gear  20  while it rotates about its own axis. Through this speed-reduction mechanism, rotation of the armature is reduced and transmitted to the carrier  18 .  
     [0072] In general, the starter  1   b  having the speed reduction device  17  produces a large torque and is subjected to a large unbalanced load applied on the pinion gear  6  when the ring gear  16  meshes with the pinion gear  6 . Hence, the twist if caused due to inclination of the pinion shaft  5  induces a large loss. Accordingly, the starter  1   b  having the speed reduction device  17  provides a plurality of bearings  14  for preventing the pinion shaft  5  from inclining. Thus, the driving loss can be effectively reduced.  
     [0073] It is needless to say that the speed reduction device  17  can be equally incorporated in the starter of the above-described first or second embodiment.  
     [0074] The rest of the starter  1   b  according to the third embodiment is substantially the same as that of the starter  1  disclosed in the first embodiment.  
     Fourth Embodiment  
     [0075] The rolling-contact bearings of the present invention are not limited to the ball bearings disclosed in the above-described first to third embodiments. For example, it is possible to replace the ball bearings by other type of bearings, such as roller bearings having rollers or needles respectively serving as rolling members.