JPH045733Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] This invention relates to an improvement of an internal reduction type starter incorporating a planetary gear reduction device.

[Prior Art] Conventionally, there has been a device of this type as shown in Japanese Utility Model Application Publication No. 58-96123. Hereinafter, the relationship diagram will be reproduced in FIG. 1 and will be summarized and explained.

Conventionally, there has been a motor for starting an engine as shown in FIG. In FIG. 1, reference numeral 1 denotes a DC motor. A front bracket 6 is fixed to the front end of a cylindrical yoke 2 of the motor 1, and an internal gear 3 of a gear reduction mechanism 7 is mounted on the inner peripheral surface of the bracket 6. An intermediate bracket 4 is fitted together with a rubber ring 6. An armature rotating shaft 9 is fitted into the armature 8 of the DC motor 1 , and a spur gear 10 is provided at the front end of the rotating shaft 9 projecting from the yoke 2 . It is meshed with. The planetary gear 11 is rotatably supported by a support pin 13 via a bearing 12 and meshed with the internal gear 3. The support pin 13 is fixed to the flange 14, and the support pin 13 is fixed to the flange 14.
4 is formed integrally with the output rotating shaft 15. A sleeve bearing 16 is fitted onto the inner peripheral surface of the intermediate bracket 4, and the sleeve bearing 16 pivotally supports the output rotating shaft 15. Output rotation shaft 15
A sleeve bearing 1 is installed in the recess 18 on the inner peripheral surface of the rear end.
7 is fitted, and the sleeve bearing 17 pivotally supports the front end of the armature rotating shaft 9. A steel ball 19 is disposed between the front end of the armature rotating shaft 9 and the rear end of the output rotating shaft 15 arranged on the axial extension of the rotating shaft 9.
is interposed therebetween, and the steel ball 19 has the function of transferring thrust loads from both rotating shafts 9 and 15. In addition, in Fig. 1, 20, 21, 22 are thrust washers,
Reference numeral 23 denotes a helical spline formed on the outer peripheral surface of the output rotating shaft 15, and an overrun clutch (not shown) is engaged with the spline.

Next, the operation of the engine starting electric motor as described above will be explained. The armature 8 is energized and generates rotational force, and this rotational force is transmitted from the armature rotating shaft 9 to the flange 14 via the spur gear 10, the planetary gear 11, and the support pin 13, and is transmitted by the planetary gear mechanism 7. The rotational speed of the armature 8 is reduced and transmitted to the output rotating shaft 15.

[Problems to be Solved by the Invention] Such conventional starters have the drawbacks of a relatively short life as a starter and a large meshing noise (particularly at high rotations under no load).

The purpose of the invention is to obtain a starter with long life and low noise.

[Means for Solving the Problems] In order to achieve the above object, the present invention is an internal reduction type starter having a built-in planetary gear reduction device,
A rotating shaft 28 of the power unit is supported by a rear end of an output rotating shaft 30 via a first sleeve bearing 32, and a planetary gear reduction gear is mounted on a flange 39 integrally formed with the rear end of the output rotating shaft 30. A support pin 38 is fitted and supported, and a second sleeve bearing 40 is interposed between the rear end of the output rotating shaft 30 and the intermediate machine frame 36, and a spur gear 33 provided at the front end of the rotating shaft 28 and In an internal reduction type starter in which a planetary gear 34 supported by the support pin 38 is meshed, an internal gear 35 is integrally provided in the intermediate machine frame 36, and the planetary gear 34 is internally meshed with the internal gear 35. The reduction gear reduces the backlash of the gear engagement part to 0.1 of the module value that makes up the tooth profile.
The clearance between the second sleeve bearing 40 and the bearing portion 42 at the rear end of the output rotating shaft 30 is
It is an object of the present invention to provide an internal reduction type starter characterized in that the backlash is configured to be one-half or less of the backlash formed by the internal gear 35 and the internal gear 35.

[Embodiment of the invention] An embodiment of the invention will be described below with reference to FIG.

In Fig. 2, 24 is an internal reduction type starter;
25 is a DC motor, 26 is a yoke, 27 is an armature,
Reference numeral 28 denotes the rotation shaft of the armature 27, and the front end bearing portion 29 is connected to the first sleeve bearing 32 fitted in the groove 31 provided at the rear end of the output rotation shaft (pinion shaft) 30. It is then supported on the shaft. 33 is a spur gear formed integrally with the rotating shaft 28,
The planetary gears 34 are always meshed. Reference numeral 35 denotes an internal gear with which the planetary gear 34 is internally meshed, and is constructed integrally with the intermediate machine frame 36. 37 is planetary gear 3
The sleeve bearing is fitted into the through hole 34a of No. 4, through which the support pin 38 is inserted, and the planetary gear 34 is supported. The support pin 38 has a flange 39 integrated with the rear end of the pinion shaft 30.
is fitted into the A second sleeve bearing 40 is fitted into a central through hole 41 of the intermediate machine frame 36, and loosely supports a bearing portion 42 disposed at the rear of the pinion shaft 30. 43 is a steel ball, and 44 is a helical spline formed on the output rotating shaft 30, into which an overrunning clutch 45 is spline-fitted so as to be slidable back and forth. 46 is a pinion, 47 is a stopper attached to the front end of the output rotating shaft 30, and 48 is a supported part provided at the front end of the output rotating shaft 30, which is supported by a sleeve bearing (not shown). . 49 is the front machine frame. In addition, in the planetary gear reduction device composed of the spur gear 33, the planetary gear 34, the internal gear 35, the support pin 38, and the flange 39, the backlash of the gear engagement portion is 0.1 to 0.2 times the module value of the tooth profile. is set to Furthermore, the bearing part 2 on the rotating shaft 28
The clearance between the first sleeve bearing 32 and the first sleeve bearing 32 is set to a value that is one-half or less of the amount of backlash described above. Further, the clearance between the second sleeve bearing 40 and the supported portion 42 disposed at the rear of the output rotating shaft 30 is also configured to have the same value as described above.

In short, this invention satisfies the following requirements in the configuration described above. In other words, the backlash of the reduction gear part of the planetary gear reduction type starter is 0.1M to 0.2M (where M is the gear module value).
() The clearance formed between the bearing metal [second sleeve bearing 40] having the same rotation center as the internal gear 35 and the supported part 42 on the output rotating shaft 30 is defined as the clearance between the planetary gear 34 and the internal gear. 35 or less of the above backlash value.

() The clearance between the front end bearing portion 29 of the rotating shaft 28 of the armature 27 and the first sleeve bearing 32 that supports the shaft is determined by the above-mentioned backlash value formed between the spur gear 33 and the planetary gear 34. It shall be less than one-half of

() The clearance of the bearing metal [second sleeve bearing 40] in () above is adjusted to the metal [first sleeve bearing 32] in () above.
The clearance shall be smaller than that of the

[Effect of the invention] The backlash of the gear engagement portion of the planetary gear 34 is configured to be 0.1 to 0.2 times the module value that constitutes the tooth profile of the planetary gear reduction gear, and the FIG. 3 shows the experimental results when the gap between the rear end and the bearing part 42 was set to 1/2 or less of the backlash formed by the planetary gear 34 and the internal gear 35.

In this figure 3, a backlash is performed using an internal reduction type starter using a module 1.15 planetary gear.
The results of an experiment on the bearing clearance and starter life (in this case, the number of engine starts) when set to 0.17mm are shown.

In this case, the life span refers to the first sleeve bearing 32 and the second sleeve bearing 32 in the embodiment of the present invention shown in FIG.
As the wear of the sleeve bearing 40 increases, the eccentricity of the flange 39 increases and the teeth of the planetary gear 34, internal gear 35, and spur gear 33 are damaged, making it impossible to perform the starter function. Furthermore, when the first sleeve bearing 32 and the second sleeve bearing 40 become severely worn, the first sleeve bearing 32 and the second sleeve bearing 40 will seize, and the flange 39 and output shaft 30 will no longer be able to rotate, and will no longer function as a starter. It disappears.

Figure 4 shows backlash 0.17mm (0.15M)
In addition to (Fig. 3), the thickness is 0.09mm.
(0.08M) and a backlash of 0.25mm (0.22M).

The following can be seen from Figure 4 or Figure 5.

(1) In the case of 0.22M (backlash 0.25mm),
If the backlash of the planetary gear 34 is too large, the rattling between the planetary gear 34 and the internal gear 35 will be severe, the life will be shortened, and the noise will be loud, so an appropriate upper limit is 0.2M.

(2) In the case of 0.08M (backlash 0.09mm),
Even if the planetary gear 34 and the internal gear 35 are manufactured so that the backlash between the planetary gear 34 and the internal gear 35 is 0.09 mm, the flange 39, intermediate machine frame 36, and yoke 26 to which they are attached are , since the accuracy of each part such as the front machine frame 49 will not be achieved, the total manufacturing error will be large after each part is assembled, and the life will not be improved much, so the lower limit is
0.1M is appropriate. Theoretically, the smaller the crushing is, the better, but in practice, in a starter, only the planetary gear has a crushing of 0.09 mm.
Even if it is set to (0.08M), good results will not be obtained because the accuracy of other individual parts is poor as mentioned above.

(3) In the case of 0.15M (backlash 0.17mm),
The backlash value of the planetary gear is extremely easy to manufacture due to the precision of each part, and since the backlash between the planetary gear and the internal gear is reduced, the life is increased and the noise is reduced, and it is 0.1M ~ 0.2M is optimal.

As described above, according to the present invention, by configuring the backlash of the gear engagement portion of the planetary gear 34 to be 0.1 to 0.2 times the module value constituting the tooth profile of the planetary gear reduction device, the planetary gear, Each tooth of the internal gear and the spur gear will not be damaged, and the life of the starter can be extended.

Further, the clearance between the second sleeve bearing 40 and the supported portion 42 at the rear end of the output rotating shaft 30 is set to be less than one-half of the backlash formed by the planetary gear 34 and the internal gear 35. in,
Since the eccentricity of the intermediate machine frame 36 with respect to the output rotating shaft 30 is reduced, the rattling of the internal gear 35, which is provided integrally with the intermediate machine frame 36, is reduced, and as a result, the internal gear 35 and Meshing noise with the planetary gear 34 is also reduced.

Figure 5 shows the experimental results showing that the meshing noise is reduced, and shows the noise data during no-load operation of the starter with a backlash of 0.17mm and a backlash of 0.17mm.
The cases of 0.25 mm and 0.09 mm of backlash are shown.

FIG. 6 shows the measurement method used in that case.

As described above, the present invention has the advantage that the planetary gear is not damaged, the starter can have a long life, and the noise caused by meshing can be reduced.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view showing the main parts of a conventional device, Fig. 2 is a half-sectional view of main parts of an internal reduction type starter according to an embodiment of the present invention, and Figs. 3, 4, and 5 are the main parts of the present invention. FIG. 6 is a diagram illustrating the measurement method used to obtain the experimental results shown in FIG. 5. In the figure, 28 is a rotating shaft, 30 is an output rotating shaft, 32 is a first sleeve bearing, 33 is a spur gear, 34 is a planetary gear, 35 is an internal gear, and 40 is a second sleeve bearing.

Claims (1)

[Claims for Utility Model Registration] (1) This is an internal reduction type starter with a built-in planetary gear reduction device, in which the rotating shaft 28 of the prime mover is connected to the rear end of the output rotating shaft 30 via a first sleeve bearing 32. Further, a support pin 38 of the planetary gear reduction device is fitted and supported by a flange 39 integrally formed at the rear end of the output rotation shaft 30, and further, the rear end of the output rotation shaft 30 and the intermediate machine frame 3 are supported.
A second sleeve bearing 40 is interposed between 6 and 6, and a spur gear 33 is provided at the front end of the rotating shaft 28.
and a planetary gear 34 supported on the support pin 38.
In the internal reduction type starter, an internal gear 35 is integrally provided in the intermediate machine frame 36, and a planetary gear 34 is internally engaged with the internal gear 35, and the planetary gear reduction device reduces the backlash of the gear engagement portion. 0.1 of the module value that makes up the tooth profile
~0.2 times, and the clearance between the second sleeve bearing 40 and the bearing portion 42 at the rear end of the output rotating shaft 30 is formed by the planetary gear 34 and the internal gear 35. An internal reduction type starter characterized in that the speed is less than one-half of the speed of the pump. (2) The clearance between the first sleeve bearing 32 and the rotating shaft 28 of the prime mover is reduced by two of the backlashes formed between the spur gear 33 and the planetary gear 34 formed at the front end of the rotating shaft 28 of the prime mover.
1. An internal reduction type starter according to claim 1, characterized in that the internal speed reduction starter is configured to be less than one-fold. (3) A utility model registration request characterized in that the clearance between the second sleeve bearing 40 and the rotary shaft 30 is smaller than the clearance between the first sleeve bearing 32 and the rotary shaft 28. An internal reduction type starter according to item 1 or 2 of the range.