JP2009097406A - Starter - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a starter, capable of preventing the deterioration of idle traveling performance by regulating the inclination of an output shaft by a simple constitution. <P>SOLUTION: A slide bearing 13 fixed to a center case 14 is disposed in such a way that the end surface of the bearing faces the end surface of an inner 28 so as to be capable of abutting on it. At the time of overrun, a return force acts on a pinion 6 by the reaction of a torsional spline, and the reaction causes the end surface of the inner 28 to abut on the end surface of the slide bearing 13. The inner 28 goes along the end surface of the slide bearing 13 to regulate the inclination of the output shaft 4, and whirl-around at high speed rotation is prevented to prevent the deterioration of idle traveling performance. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a starter for starting an engine.

2. Description of the Related Art Conventionally, a starter for starting an engine is provided with an output shaft having a pinion arranged on a shaft and an inner portion of a one-way clutch formed at a rear end and a slide bearing provided on a front case and a center case. There is a structure that is rotatably supported by a plain bearing (see, for example, Patent Document 1).
JP-A-9-88780

  However, when the engine is started by the starter and the engine speed exceeds the starter speed and the starter side pinion is turned over, the output shaft can be output even if the balance is slightly lost due to the inner rotating at high speed. There is a concern that the whirling that rotates in the state where the tilt is likely to occur. FIG. 5 is a schematic diagram showing how the output shaft swings. When such a swing of the output shaft occurs, noise due to vibration is generated, or the balance of the inner balance is transmitted to the outer via the roller, which causes problems such as deterioration of the idling performance of the clutch. For this reason, it has been necessary to reduce the clearance of the slide bearing and to accurately process the balance of the rotating body such as the output shaft and the outer.

  The present invention has been made in view of the above problems, and an object of the present invention is to provide a starter capable of preventing the deterioration of idling performance by regulating the inclination of the output shaft with a simple configuration.

  Hereinafter, each means suitable for solving the above-described problems will be described with additional effects and the like as necessary.

1. An output shaft having a pinion disposed on the shaft, a planetary gear speed reduction device that reduces the rotational speed of the motor, an outer that is integrated with a planet carrier of the planetary gear speed reduction device and rotates by receiving the revolution force of the planetary gear, An inner portion formed at the rear end of the output shaft, a one-way clutch comprising a roller interposed between the outer and the inner, an outer periphery of the planetary gear reduction device and the one-way clutch and covering the output shaft In a starter provided with a center case provided with a sliding bearing that is rotatably supported,
The starter characterized in that the sliding bearing is disposed so as to be able to contact the inner.

  According to the means 1, the sliding bearing that rotatably supports the output shaft is disposed so as to be able to contact the inner formed at the rear end of the output shaft. When the return force acts and the inner surface abuts on the sliding bearing by the reaction, the inclination of the output shaft is restricted, and the whirling during high-speed rotation can be prevented and the deterioration of the idling performance can be prevented.

  2. 2. The starter according to claim 1, wherein the sliding bearing is disposed so that an end surface thereof can abut against an end surface of the inner.

  According to the means 2, the sliding bearing is arranged so that its end face can be brought into contact with the end face of the inner, so that a return force acts on the pinion by the reaction force of the torsion spline at the time of overrun. Since the end surface of the inner ring contacts the end surface of the sliding bearing, the inner shaft regulates the inclination of the output shaft following the end surface of the sliding bearing, thereby preventing the whirling during high-speed rotation and preventing the deterioration of the idling performance.

3. A washer for preventing the inner from slipping out in the axial direction with respect to the outer;
The starter according to claim 2, wherein the sliding bearing is disposed so as to overlap with an inner diameter side of the washer.
According to the means 3, since the sliding bearing is disposed so as to overlap the inner diameter side of the washer that prevents the inner from coming out in the axial direction with respect to the outer, the sliding bearing is disposed between the inner diameter of the washer and the outer diameter of the output shaft. By forming a space and acting as an oil reservoir, the lubricating oil filled between the sliding bearing end face and the inner end face is prevented from splashing to the outside due to centrifugal force, thereby improving seizure resistance. Can do.

  4). When the gap between the inner end face and the slide bearing end face in the state where the output shaft is located at the rearmost position with respect to the center case is a and the plate thickness of the washer is b, a <b The starter according to claim 3, wherein: is established.

  According to the means 4, the gap a between the inner end face and the sliding bearing end face in a state where the output shaft is located at the rearmost position with respect to the center case is smaller than the plate thickness b of the washer. Regardless of the fact that the washer and the sliding bearing always overlap each other, the lubricating oil can be retained without being scattered outside by centrifugal force.

  5). 5. The starter according to any one of means 2 to 4, wherein the sliding bearing is provided with a flange portion projecting radially outward at a rear end portion thereof.

  According to the means 5, since the flange portion projecting radially outward is provided at the rear end portion of the slide bearing, the contact diameter with the inner end surface is not increased without increasing the diameter of the slide bearing provided in the center case. By increasing, the inclination of the output shaft can be more reliably suppressed.

  6). The starter according to claim 5, wherein the sliding bearing has a chamfered inner diameter of the collar portion.

  According to the means 6, since the chamfer is provided on the inner diameter of the flange portion projecting outward in the radial direction, the oil clogging effect can be further improved by setting the chamfer of the bearing inner diameter portion large. Further, by setting a large corner R at the boundary between the output shaft and the inner, it is possible to facilitate processing and improve the strength of the output shaft.

7). The inner is provided with a concave groove along the outer periphery of the output shaft at a front end portion thereof,
The starter according to claim 1, wherein the slide bearing is disposed so that at least a part thereof is fitted in the concave groove of the inner.

  According to the means 7, the inner is provided with a concave groove along the outer periphery of the output shaft at the front end portion thereof, and the slide bearing is arranged so that at least a part thereof fits into the concave groove of the inner. When the rear end of the bearing abuts against the inner wall surface of the groove, the inclination of the output shaft is regulated, and it is possible to prevent the whirling during high speed rotation and prevent the deterioration of the idling performance, and the sliding bearing and the inner The oil retaining effect of the lubricating oil filled during the period can be improved.

  DESCRIPTION OF EMBODIMENTS Hereinafter, an embodiment embodying a starter of the present invention will be specifically described with reference to the drawings. FIG. 1 is an axial sectional view showing a starter 1 according to an embodiment of the present invention. FIG. 2 is an axial sectional view showing the periphery of the clutch in the starter 1 of FIG. 1 in an enlarged manner.

  The starter 1 of the present embodiment is arranged on the same axis as the armature shaft 2 on the front side (left side in FIG. 1) of the motor 3 that receives energization and generates a rotational force on the armature shaft 2. The output shaft 4, a pinion 6 that is torsionally spline-fitted to the outer periphery of the output shaft 4, a planetary gear reduction device (described later) that reduces the rotational speed of the motor 3, and the rotational force is transmitted from the planetary gear reduction device to the output shaft 4 A one-way clutch (to be described later), a magnet switch 7 that generates electricity for the motor 3 and a pushing force for the pinion 6.

  The motor 3 includes an armature 8 having an armature shaft 2, a fixed magnetic pole 9 disposed on the outer periphery of the armature 8, a cylindrical yoke 10 that fixes the fixed magnetic pole 9 to the inner peripheral surface, and the like. When the switch is turned on and a contact (not shown) built in the magnet switch 7 is closed, the armature 8 is energized to rotate.

  The output shaft 4 has a front end portion rotatably supported by a front end portion of a front case 12 via a slide bearing 11 and a rear end side rotatably supported by a center case 14 via a slide bearing 13. The slide bearing 13 is fixed in a state in which the rear end portion protrudes from the inner diameter of the small diameter cylindrical portion 14 a provided at the front end of the center case 14.

  A hollow cylindrical recess along the axial direction is formed at the center of the rear end of the output shaft 4, and a slide bearing 15 is disposed in the recess to rotatably support the tip of the armature shaft 2. Yes. The center case 14 covers the outer periphery of the planetary gear reduction device and the one-way clutch, is sandwiched between the front case 12 and the end case 16 together with the yoke 10, and is entirely fixed by a plurality of through bolts 17. Yes.

  The pinion 6 is provided integrally with a spline tube 18 that is twisted and spline-fitted to the outer periphery of the output shaft 4. The pinion 6 can mesh with the ring gear 20 of the engine by the spline tube 18 being twisted on the output shaft 4 via the lever 19 and pushed forward along the spline. One end of the lever 19 is engaged with the outer periphery of the spline tube 18, and the other end is engaged with a rod 21 that protrudes toward the distal end side of the magnet switch 7. It is supported by.

  The planetary gear reduction device is a reduction device that increases the output torque by reducing the rotational speed of the motor 3. The planetary gear reduction device includes a sun gear 22 formed on the outer periphery of the armature shaft 2, three planetary gears 23 that mesh with the sun gear 22, An internal gear 24 meshing with the planetary gear 23 and a planet carrier 25 to which the revolution force of the planetary gear 23 is transmitted. The sun gear 22 rotates integrally with the armature shaft 2 to transmit the rotation of the armature shaft 2 to the three planetary gears 23.

  The three planetary gears 23 are rotatably supported by pins 26 fixed to the planet carrier 25 via bearings 27 and revolve around the outer periphery of the sun gear 22 while meshing with the sun gear 22 and the internal gear 24. The internal gear 24 is formed on the inner peripheral surface of the cylindrical wall of the center case 14. The planet carrier 25 is integrated with the outer of the one-way clutch (same as the planet carrier 25), and rotates with the revolution force of the planetary gear 23 transmitted thereto. Three pins 26 are fixed to the planet carrier 25.

  The one-way clutch includes an outer 25, an inner 28, a roller 29, a spring (not shown), and the like. The outer 25 has a plurality of wedge-shaped cam chambers (not shown) formed on the inner peripheral surface thereof, and accommodates the rollers 29 in the cam chambers. A plurality of cam chambers are provided at equal intervals in the circumferential direction of the outer 25.

  Further, the one-way clutch includes a washer 30 for preventing the inner 28 from coming off and preventing the lubricating grease from flowing out. The washer 30 has an outer peripheral portion that contacts the end face of the outer 25 fixed by the clutch cover 31 and an inner peripheral portion that contacts the inner 28, thereby restricting the inner 28 from coming out in the left direction in the drawing and flowing out the grease. Is preventing.

The inner 28 is provided with a rear end portion of the output shaft 4 enlarged in the radial direction. The roller 29 is provided in a cylindrical shape. When the outer 25 rotates, the roller 29 is pressed toward the narrower side of the cam chamber and locks the outer 25 and the inner 28 to transmit the rotation of the outer 25 to the inner 28. The spring is housed in the cam chamber together with the roller 29, and presses the roller 29 toward the narrower side of the cam chamber.
Here, the sliding bearing 13 is fixed to the inner periphery of the small-diameter cylindrical portion 14a at the tip of the center case 14 in a state in which the rear end protrudes, and the end surface of the sliding bearing 13 is disposed so as to be in contact with the end surface of the inner 28. At the same time, it is disposed so as to overlap the inner diameter side of the washer 30.

  In addition, as shown in FIG. 2, the gap between the end face of the inner 28 and the end face of the slide bearing 13 in a state where the output shaft 4 is located at the rearmost position with respect to the center case 14 is a, and the plate thickness of the washer 30 is b. Then, the relationship of a <b is established.

  The magnet switch 7 attracts a plunger (not shown) accommodated in the switch by a magnetic force generated in the coil when the starter switch described above is turned on and a built-in coil (not shown) is energized. As a result, the contact of the motor 3 is closed and the lever 19 is swung through the rod 21 to generate the pushing force of the pinion 6.

  Next, the operation of the starter 1 will be described. When the starter switch is turned on, the contact of the motor 3 is closed by the magnet switch 7 and the armature 8 is energized, whereby a rotational force is generated in the armature 8. As a result, the sun gear 22 rotates together with the armature shaft 2 to rotationally drive the three planetary gears 23. Each planetary gear 23 meshes with the sun gear 22 and the internal gear 24. However, since the internal gear 24 is provided in the center case 14 and does not rotate, each planetary gear 23 rotates around the pin 26. While rotating the outer periphery of the sun gear 22. This revolution force is transmitted to the planet carrier 25 (that is, the outer 25) through the pin 26, and the rotation of the outer 25 is transmitted to the inner 28 through the roller 29, whereby the output shaft 4 is rotationally driven.

  On the other hand, the pinion 6 fitted to the output shaft 4 is pushed forward (to the left in the drawing) on the shaft of the output shaft 4 integrally with the spline tube 18 via the lever 19 by the attractive force of the magnet switch 7. By engaging with 20, the rotational force of the motor 3 is transmitted to the ring gear 20. Thereafter, when the engine is started and the pinion 6 is rotated at a high speed by the ring gear 20, the rotation of the inner 28 becomes faster than the rotation of the outer 25, but the roller 29 between the inner 28 and the outer 25 has a wide cam chamber. When the inner 28 and the outer 25 are unlocked by moving in the direction, the rotational force is not transmitted from the inner 28 to the outer 25, and overrun of the armature 8 can be prevented.

  As is apparent from the above detailed description, according to the present embodiment, the output shaft 4 having the pinion 6 disposed on the shaft, the planetary gear reduction device that reduces the rotational speed of the motor 3, and the planetary gear reduction device. The outer carrier 25 that is integrated with the planet carrier 25 and rotates by receiving the revolving force of each planetary gear 23, the inner 28 formed at the rear end of the output shaft 4, and the roller 29 interposed between the outer 25 and the inner 28. In the starter 1, the sliding bearing 13 includes a planetary gear reduction device and a center case 14 provided with a sliding bearing 13 that covers the outer periphery of the planetary gear reduction device and the one-way clutch and that rotatably supports the output shaft 4. Since the end face is arranged so as to be able to come into contact with the end face of the inner 28, the return force acts on the pinion 6 by the reaction force of the torsion spline at the time of overrun. As a result, the end face of the inner 28 comes into contact with the end face of the sliding bearing 13, and the inclination of the output shaft 4 is regulated so that the inner 28 follows the end face of the sliding bearing 13, thereby preventing the whirling during high-speed rotation and deteriorating the idling performance. Can be prevented.

  Further, since the slide bearing 13 is disposed so as to overlap the inner diameter side of the washer 30 that prevents the inner 28 from coming out in the axial direction with respect to the outer 25, the inner diameter of the washer 30 and the outer diameter of the output shaft 4 are arranged. By forming a space between them and acting as an oil reservoir, the lubricating oil filled between the end face of the slide bearing 13 and the end face of the inner 28 is prevented from being scattered to the outside by centrifugal force, and has seizure resistance. Improvements can be made.

  Further, the gap a between the end face of the inner 28 and the end face of the sliding bearing 13 in a state where the output shaft 4 is positioned toward the rearmost side with respect to the center case 14 is smaller than the plate thickness b of the washer 30 (a <b). Regardless of the position of the output shaft 4 in the axial direction, the washer 30 and the sliding bearing 13 always overlap each other, so that the lubricating oil can be retained without being scattered by the centrifugal force.

  Needless to say, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  For example, it is good also as a structure which provides the collar part 13a which protrudes in a radial direction at the rear-end part of the sliding bearing 13 like the 1st modification shown in FIG. FIG. 3 is an axial sectional view showing the periphery of the clutch in the first modification. According to this modification, the inclination of the output shaft 4 can be more reliably suppressed by increasing the contact diameter with the end face of the inner 28 without increasing the diameter of the sliding bearing 13 provided in the center case 14. Can do. Further, in this modified example, since the chamfer 13b is provided on the inner diameter of the flange portion 13a projecting outward in the radial direction, the oil clogging effect can be further improved by setting the chamfer of the inner diameter portion of the slide bearing 13 large. . Further, by setting the corner R at the boundary between the output shaft 4 and the inner 28 to be large, the processing becomes easy and the strength of the output shaft 4 can be improved.

  Moreover, in the said embodiment, although it was set as the structure by which the end surface of the sliding bearing 13 opposes the end surface of the inner 28 so that contact | abutment is possible, the front end part of the inner 28 is shown like the 2nd modification shown in FIG. Is provided with a groove 28a along the outer periphery of the output shaft 4, and at least a part of the slide bearing 13 (specifically, the rear end portion of the slide bearing 13) is disposed so as to fit into the groove 28a of the inner 28. It is good. FIG. 4 is an axial sectional view showing the sliding bearing 13 and the inner 28 in the second modification. According to this modification, the rear end portion of the sliding bearing 13 abuts against the inner wall surface of the concave groove 28a, so that the inclination of the output shaft 4 is restricted, preventing the whirling during high-speed rotation and preventing the idling performance from deteriorating. In addition, the oil retaining effect of the lubricating oil filled between the slide bearing 13 and the inner 28 can be improved. In short, if the sliding bearing 13 is arranged so as to be able to come into contact with the inner 28, a return force acts on the pinion 6 by the reaction force of the torsion spline at the time of overrun, and the inner 28 comes into contact with the sliding bearing 13 by the reaction. As a result, the inclination of the output shaft 4 is restricted, and the whirling during high-speed rotation can be prevented and the deterioration of the idling performance can be prevented.

  In the starter in which the planet carrier of the planetary gear reduction device and the outer of the one-way clutch are integrated, it is necessary to regulate the inclination of the output shaft and prevent the idling performance from being deteriorated. Is available.

It is an axial sectional view showing a starter of one embodiment of the present invention. FIG. 2 is an axial cross-sectional view showing an enlarged periphery of a clutch in the starter of FIG. 1. It is an axial direction sectional view showing the clutch circumference in the 1st modification. It is an axial direction sectional view showing a slide bearing and an inner in the 2nd modification. It is a schematic diagram for demonstrating the swing of the output shaft in a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Starter 3 Motor 4 Output shaft 6 Pinion 13 Slide bearing 13a Collar part 13b Chamfer 14 Center case 23 Planetary gear 25 Planet carrier, outer 28 Inner 28a Concave groove 29 Roller 30 Washer

Claims (7)

An output shaft having a pinion disposed on the shaft, a planetary gear speed reduction device that reduces the rotational speed of the motor, an outer that is integrated with a planet carrier of the planetary gear speed reduction device and rotates by receiving the revolution force of the planetary gear, An inner portion formed at the rear end of the output shaft, a one-way clutch comprising a roller interposed between the outer and the inner, an outer periphery of the planetary gear reduction device and the one-way clutch and covering the output shaft In a starter provided with a center case provided with a sliding bearing that is rotatably supported,
The starter characterized in that the sliding bearing is disposed so as to be able to contact the inner. The starter according to claim 1, wherein an end surface of the slide bearing is disposed so as to be able to abut against an end surface of the inner. A washer for preventing the inner from slipping out in the axial direction with respect to the outer;
The starter according to claim 2, wherein the sliding bearing is disposed so as to overlap with an inner diameter side of the washer.   When the gap between the inner end face and the slide bearing end face in the state where the output shaft is located at the rearmost position with respect to the center case is a and the plate thickness of the washer is b, a <b The starter according to claim 3, wherein: is established.   The starter according to any one of claims 2 to 4, wherein the sliding bearing is provided with a flange portion projecting radially outward at a rear end portion thereof.   The starter according to claim 5, wherein the sliding bearing is provided with a chamfer on an inner diameter of the collar portion. The inner is provided with a concave groove along the outer periphery of the output shaft at a front end portion thereof,
2. The starter according to claim 1, wherein at least a part of the plain bearing is fitted in the concave groove of the inner.