JPH09310667A - Starter with planetary gear reduction mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To ease shock load such as meshing shock, and reduce noise caused by a backlash at the time of starting an engine. SOLUTION: A starter has a planetary gear reduction mechanism 6 which is composed of an internal gear 2 movably held inside the center cas 12 of a driving housing 1; a sun gear 3 rotatingly driven by a motor; a planetary gear 4; and a driving shaft 5 to hold the planetary gear 4. An irregular face 7 having irregularities arranged in a peripheral direction is formed on the front end face of the internal gear 2, and a spring 8 formed of a plate spring is fixed in the center case 12 opposite to the irregular face 7. The spring 8 is pressingly energized to abut against the irregular face 7. When excessive torque acts on the internal gear 2, it rotates to ease shock load. When the torque fluctuates within a fixed range, the internal gear 2 is reciprocatingly rotated by the elastic force of the spring 8, and backlash noise is thereby prevented.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention belongs to the technical field of starters for starting an engine.

[0002]

2. Description of the Related Art A starter mounted on a vehicle such as an automobile in recent years is required to be downsized because the inside of an engine room is highly dense, and at the same time, it is required to be lightweight for the purpose of improving fuel consumption. Has been done. Therefore, small and lightweight internal reduction type starters are now mainstream, and this trend is expected to increase in the future.

The internal deceleration type starter is equipped with a small and lightweight high speed rotation motor and a deceleration mechanism for decelerating the rotation of the motor to increase the torque, so that the starter can be operated without reducing the shaft output at the time of starting. It is a smaller and lighter version of. There are several types of speed reduction mechanism,
Among them, the planetary gear reduction mechanism is suitable for reduction in size and weight because a relatively high reduction ratio can be obtained. A starter with a built-in planetary gear reduction mechanism is called a starter with a planetary gear reduction mechanism.

In order to reduce the size and weight, it is effective to drive the pinion by increasing the torque with a speed reducing mechanism having a high speed reducing ratio by a starter motor that rotates at a high speed even with a low torque, while reducing the speed reducing ratio of the speed reducing mechanism. There is a penalty in raising it. That is, when the reduction ratio is high, the starter motor can be downsized, and the moment of inertia of the armature is also reduced. However, when observed from the side of the drive shaft that drives the pinion, the equivalent moment of inertia of the armature increases in proportion to the square of the reduction ratio, so the higher the reduction ratio, the greater the moment of inertia around the drive shaft.
As a result of the increase in the moment of inertia around the drive shaft, the impact (meshing impact) that occurs at the moment when the rotating starter pinion gear meshes with the ring gear on the engine side becomes more intense, increasing the impact load applied to the reduction mechanism. There is. As a result, there is a problem that the requirements for strength of the reduction gear mechanism, the housing, the mounting portion of the starter, and the like become strict, and the weight reduction effect due to the high reduction ratio may be diminished.
In addition, the noise generated due to the meshing impact also increases, which causes a problem of sound insulation.

The present applicant has developed the technique disclosed in Japanese Patent Laid-Open No. 63-277859 for the purpose of solving these problems, and has already applied to the market a product in which the technique is applied to a starter with a planetary gear reduction mechanism. Are being sent to. This starter with a planetary gear reduction mechanism (prior art) is a friction disk that rotates together with the internal gear of the planetary gear reduction mechanism,
And a member for sandwiching the disc with a predetermined pressing force.
Since this member is fixed to the housing, when torque is applied to the internal gear, a friction torque is generated as a reaction force between the internal gear and the friction disc, and until the torque applied to the internal gear exceeds a predetermined value, Do not allow the internal gear to rotate. When an excessive torque is applied to the internal gear due to a meshing impact or the like, a slip occurs between the member and the friction disk, and the internal gear rotates, so that the impact of the excessive torque is mitigated. Since the meshing impact is alleviated in this way, in the starter with the planetary gear reduction mechanism, the weight reduction of the strength member by mitigating the impact load and the noise reduction by mitigating the impact noise are realized.

[0006]

According to the starter with a planetary gear speed reduction mechanism described above, the meshing impact is alleviated, but there is a problem in that noise is generated when the engine is started due to backlash, and the noise cannot be ignored. I have left it. That is, in a starter with a planetary gear speed reduction mechanism, as compared with a starter without a speed reduction mechanism, there are more sun gears, planetary gears, and internal gears and gears that make up the planetary gear speed reduction mechanism, and there are more meshes thereof. Therefore, since the backlash generated at the meshing portion of the gears overlaps, the total backlash is considerably larger than that of the starter without the reduction mechanism.

On the other hand, in a normal piston engine, the load torque fluctuates as the crankshaft rotates. The sign of the load torque may be inverted between positive and negative depending on the angular position of the crankshaft. The flywheel is provided for the purpose of suppressing the pulsation of the crankshaft angular velocity due to the load torque fluctuation, but the pulsation of the angular velocity (that is, the angular acceleration that periodically changes between positive and negative) cannot be zero.

Therefore, the flywheel whose angular velocity pulsates may accelerate the pinion gear of the starter conversely via the ring gear formed on the outer periphery of the flywheel.
In that case, noise due to backlash occurs. As described above, in the starter with the planetary gear speed reduction mechanism, the backlash is large and the equivalent moment of inertia is also large due to the high reduction ratio, so the generated noise may be too large to be ignored.

That is, in the conventional starter with a planetary gear speed reduction mechanism, there is a disadvantage that a noise due to the backlash is generated at the time of engine start, and the noise is larger than the starter without the speed reduction mechanism because the backlash is large. Therefore, the present invention is to solve the problem to provide a starter with a planetary gear reduction mechanism in which noise (hereinafter referred to as backlash noise) generated due to backlash in the starter at engine startup is reduced. To do.

[0010]

Means for Solving the Problems and Their Functions and Effects In order to solve the above problems, the inventors have invented the following means. (First Means: Uneven Surface on One Side) The first means of the present invention is a starter with a planetary gear speed reduction mechanism according to any one of claims 1 and 2.

According to the present means, the internal gear is held so that the internal gear is held in the housing in any one of three states: a static engagement state, a rotational displacement engagement state, and a transit state. ing. The starter with planetary gear reduction mechanism of this means has the planetary gear reduction mechanism configured in this way, and therefore the relationship between the housing and the internal gear depends on the torque applied from the planetary gear to the internal gear as follows. Street conditions occur.

The first state is a no-load state, in which torque is not applied to the internal gear, and the internal gear is fixed to the housing in a static engagement state. The second state is a normal load state, in which torque is applied to the internal gear, but torque as large as meshing impact torque is not applied. Therefore, although the internal gear slightly rotates when a torque larger than a predetermined initial torque is applied, the rotation restricting torque increases by the rotational displacement with respect to the housing, and the rotation of the internal gear stops. That is, when the torque applied to the internal gear is larger than the initial torque and smaller than the limiting torque, the internal gear rotates only by a displacement corresponding to the torque.

As a result, in this normal load state, the internal gear of this means stops with respect to the housing without continuing rotation (sliding). Therefore, in the above normal load state, the motor shaft output is transmitted to the drive shaft through the planetary gear speed reduction mechanism with a small loss as in the planetary gear speed reducer starter in which the internal gear is fixed to the housing even in this means. To be done.

The third state is an excessive load state. In this state, an excessive torque equal to or larger than the limit torque is applied to the internal gear, such as meshing impact torque, and the internal gear rotates with respect to the housing. Therefore, the excessive load applied to the internal gear is absorbed by the rotation of the internal gear and is not directly transmitted to the housing, so that the impact load applied to the starter is alleviated. Further, the impact torque transmitted to the sun gear connected to the armature shaft of the motor is also reduced by the rotation of the internal gear.

Therefore, according to this means, it is possible to absorb an impact load such as a meshing impact, and it is not necessary to make strict requirements for the strength of each constituent member. Therefore, a lightweight and compact starter with a planetary gear reduction mechanism can be manufactured at a low cost. Can be provided to. When the overloaded state ends, the internal gear quickly returns to the normal loaded state or the unloaded state described above in which the internal gear does not rotate.

The fourth state is a fluctuating load state, in which the load torque applied to the drive shaft fluctuates as the crankshaft of the engine rotates, and the load value takes not only a positive value but a zero or negative value. Is. In this state, the direction of the torque applied to the internal gear changes due to the pulsating load, and the torque fluctuates similarly to the load and intermittently takes zero or a negative value.

Then, the internal gear moves back and forth between the rotational displacement engagement states before and after sandwiching the stationary engagement state and makes a minute rotation. That is, the internal gear rotates by a relatively small rotation angle in response to torque fluctuations and reciprocates to absorb the torque fluctuations. The internal gear is applied with a predetermined rotation restricting torque with respect to the housing as the reciprocating motion of the internal gear is slight. Therefore, even if the load applied to the drive shaft intermittently takes a negative value, the meshing of the gears in the planetary gear reduction mechanism does not loosen and backlash due to backlash does not occur. As a result, in the starter with the planetary gear speed reduction mechanism of the present means, although the large reduction gear ratio has a large equivalent moment of inertia, the starting noise (backlash noise) due to the backlash hardly occurs, and it is greatly reduced.

Therefore, according to the present means, the backlash noise can be reduced as compared with the prior art, although the starter with the planetary gear speed reduction mechanism is small and lightweight as in the prior art. As a result, the noise generated by the occupants and others around the engine at the time of starting the engine is reduced as a whole. (Second Means) A second means of the present invention is a starter with a planetary gear speed reduction mechanism according to claim 3.

In the present means, a spring elastic member (hereinafter referred to as a spring) made of a leaf spring is provided on the uneven surface formed on the surface of the internal gear facing the motor (hereinafter referred to as a back surface). When they come into contact with each other, the same operational effect as the above-mentioned first means is produced. Here, it is relatively easy to form a concave-convex surface on the back surface of the internal gear during manufacturing, and the spring can be easily manufactured by stamping or pressing, and also easily fixed to the housing. Further, in the process of assembling the starter, when the internal gear is inserted into the same housing to which the spring is fixed, the spring does not hinder the insertion of the internal gear, so that the assembly is easy.

Therefore, according to this means, in addition to the effect of the above-mentioned first means, there is an effect that the manufacturing is easy and the manufacturing cost is low. Further, in this means, the uneven surface and the spring are accommodated in the narrow hollow cylindrical space that contacts the back surface of the internal gear, and the diameter of the portion of the housing that stores the internal gear can be increased. Absent. Therefore, according to this means, the increase in volume of the starter with the planetary gear speed reduction mechanism due to the provision of the uneven surface and the spring can be suppressed to a minimum.

(Third Means) A third means of the present invention is a starter with a planetary gear speed reduction mechanism according to a fourth aspect. In the present means, since the spring elastic member is a ring-shaped plate spring member having a plurality of cut and raised portions, it can be easily manufactured from a plate material of a spring alloy by a widely used processing method such as punching, punching and bending. it can. Further, since the shape is ring-like, when fixing to the housing, if at least one position is fixed, it does not rotate around the drive shaft, so the number of steps required for fixing the spring elastic member is reduced. It is possible. Therefore, according to this means, the first
In addition to the effect of the means, there is an effect that manufacturing of the starter with the planetary gear speed reduction mechanism of the present invention becomes cheap and easy.

Further, in the present means, since the plurality of cut-and-raised parts are arranged at equal intervals on the circumference, the pressing force applied to the internal gear becomes substantially uniform around the shaft. Therefore, according to the present means, in addition to the effect of the above-mentioned first means, unbalanced pressing force is not applied to the internal gear, so that there is no effect of uneven wear on the internal gear or the planetary gear. is there.

(Fourth Means) A fourth means of the present invention is a starter with a planetary gear speed reduction mechanism according to a fifth aspect. In this means, the spring elastic member is pressed against the rubber elastic member and is in contact with the uneven surface. Therefore, the spring elastic member comes into contact with the uneven surface with a force larger than the pressing force exerted only by the spring elastic member, and even if the diameter of the internal gear on which the uneven surface is formed is small, the rotation of the internal gear Produces sufficient friction or abutment force to hold down. Therefore, according to this means, in addition to the effect of the above-mentioned first means, a sufficiently powerful shock absorbing effect and backlash noise reducing effect can be obtained even with a small planetary gear reduction mechanism.

Further, the rubber elastic member has a stronger shock absorbing action and damping action than the spring elastic member. In the present means, since the rubber elastic member is in pressure contact with the spring elastic member, the rubber elastic member absorbs vibrations generated in the spring elastic member, noise in the housing, etc., and quickly attenuates them. Therefore, according to this means, in addition to the effect of the above-mentioned first means, there is an effect that the noise at the time of starting is further reduced.

(Fifth means: uneven surface on both sides) The fifth aspect of the present invention
The means is a starter with a planetary gear speed reduction mechanism according to claim 6. In the present means, the concavo-convex surfaces having the concavo-convex shape in the circumferential direction are respectively provided on the surfaces of the housing and the internal gear that face each other, and the elastic member is sandwiched between the both concavo-convex surfaces. . Therefore, when the rotational torque applied to the internal gear is extremely large, such as when the pinion gear meshes with each other, slipping or rolling occurs between the elastic member and at least one uneven surface, and the impact load is reduced. It Further, when the torque applied to the internal gear fluctuates within a predetermined range, the elastic member does not move over the convex portion of the uneven surface,
The torque fluctuation is absorbed by going up and down the slope of the uneven surface according to the fluctuating torque. As a result, it is possible to prevent the internal gear from slightly rotating in the direction opposite to the normal torque direction so as to close the space between the tooth surfaces and prevent a gap from being generated, so that the occurrence of backlash noise is prevented. The planetary gear speed reduction mechanism transmits the power of the motor to the drive shaft with low loss except when the torque applied to the internal gear is large and the elastic member moves beyond the convex portion of the uneven surface.

Therefore, according to this means, it is possible to prevent the generation of backlash noise while alleviating the meshing impact, and it is possible to obtain the same effect as that of the above-mentioned first means with a different configuration. In addition, since the elastic member is only sandwiched between the concave and convex surfaces, there is no need to fix the elastic member, and there is an effect that the number of assembling steps can be reduced. Further, since there is no possibility of failure due to a malfunction of the fixing means, there is an effect that reliability is also improved.

(Sixth Means) A sixth means of the present invention is a starter with a planetary gear speed reduction mechanism according to claim 7. In this means, since the elastic member is a ring-shaped corrugated plate made of a leaf spring, it is not only easy to manufacture, but an appropriate pressing force is generated between the uneven surface due to the spring elastic force of the leaf spring. Damping due to friction with the surface is obtained.

Therefore, according to this means, in addition to the effect of the above-mentioned fifth means, there is an effect that the elastic member is inexpensive to manufacture and sufficient damping can be obtained. (Seventh Means) A seventh means of the present invention is a starter with a planetary gear speed reduction mechanism according to claim 8. In the present means, both concave and convex surfaces are formed in a coaxial cylindrical surface shape, and the elastic member sandwiched between them is a round bar rubber elastic body (the former) or a pipe spring elastic body (the latter).

When the elastic member is the former, the rubber round bar rolls between the concave and convex surfaces and is applied to the slope of the concave and convex surface with the rotation of the internal gear. Transfers torque to the housing. When an extremely large torque is applied to the internal gear due to a meshing impact or the like, the rubber round bar rolls over the convex portion of the uneven surface and the internal gear rotates, so that the impact load is relieved. When the torque applied to the internal gear fluctuates within a predetermined range, the rubber round bar moves up and down the slope of the uneven surface according to the fluctuating torque, and the internal gear slightly reciprocally rotates to cause torque fluctuation. Absorb. As a result, it is possible to prevent the internal gear from slightly rotating in the direction opposite to the normal torque direction so as to close the space between the tooth surfaces and prevent a gap from being generated, so that the occurrence of backlash noise is prevented. The planetary gear reduction mechanism transmits the power of the motor to the drive shaft with low loss except when the torque applied to the internal gear is large and the rubber round bar rolls over the convex portion of the uneven surface as in the case of meshing impact.

Therefore, in this case as well, the same effect as the fifth means can be obtained, and since the elastic member is a round bar-shaped rubber elastic body and only rolls between the two concave and convex surfaces, the engine is further started. There is an effect that the noise of the can be silenced. On the other hand, when the elastic member is the latter,
The same impact load relaxation action and backlash prevention action are exhibited. Further, in this case, since the elastic member can be manufactured simply by cutting the pipe material, the elastic member is inexpensive. Further, since the elastic member can be formed of a material such as an alloy that is hard to wear, it is possible to provide a starter with a planetary gear speed reduction mechanism that has a longer life.

[0031]

[Example 1]

(Overall Configuration of First Embodiment) As shown in FIG. 1, a starter with a planetary gear speed reduction mechanism according to a first embodiment of the present invention moves a drive housing 1 and a pinion in order from the front when the left side in the drawing is the front. It has a drive shaft 5 for driving the bodies 53, 54, a planetary gear reduction mechanism 6 and a motor 30. Motor 3
0 is the field part 32 fixed to the inner circumference of the yoke 36.
And a rotor 31 that rotates together with the motor shaft 33. The planetary gear reduction mechanism 6 reduces the rotational speed of the shaft output of the motor 30 to a fraction and transmits it to the drive shaft 5, and drives the pinion gear 54 from the drive shaft 5 via the one-way clutch 53.

The starter also includes a drive housing 1
The magnetic switch 92 and the drive lever 93 held by When the starter is operating, the magnet switch 92 is used to drive the drive lever 93.
The one-way clutch 53 and the pinion gear 54 are pushed forward and mesh with the ring gear F on the engine side. Since the pinion gear 54 is decelerated by the motor 30 and the planetary gear speed reduction mechanism 6 as described above, the ring gear F is rotationally driven to start the engine (not shown).

(Structure of Drive Housing 1 of Embodiment 1) A motor 30 is fastened to the drive housing 1 with a planetary gear speed reduction mechanism 6 contained by a center case 12 and a plate 13 interposed therebetween. The drive housing 1 and the center case 12 of this embodiment correspond to the housing of the present invention.

The drive housing 1 is an aluminum alloy casting member, which forms the outer shape of the front end portion of the starter, and the front end portion of the magnet switch 92, the drive lever 93, the drive shaft 5, the clutch 53 and the pinion gear 54, and the center case. Holds twelve. The center case 12 is a steel plate drawing member made of a disk-shaped flat plate that connects the outer cylindrical portion and the inner cylindrical portion that are coaxial with each other, and the inner cylindrical portion pivotally supports the drive shaft 5. Here, a shaft hole is formed in the rear end of the drive shaft 5, and the front end of the motor shaft 33 is inserted therein. Therefore, the center case 12 holds the rear end of the drive shaft 5 and the front end of the motor shaft 33 directly and indirectly to the drive housing 1 and the motor case 36. Further, the center case 12 holds the plate 13 concentrically on the inner circumference of the open end (rear end) of the outer cylinder.

The plate 13 is a disk-shaped steel plate press-molded member having an edge, and is a partition wall that separates the planetary gear speed reduction mechanism 6 and the motor 30, and also serves as a front lid of the motor 30. (Structure of Planetary Gear Reduction Mechanism of First Embodiment) As shown in FIG. 2, the planetary gear reduction mechanism 6 is formed in a space formed by the center case 12 and the plate 13 described above, and each member has a predetermined structure. It is held so that it can operate. That is, the planetary gear reduction mechanism 6 includes an internal gear 2, a sun gear 3, a plurality of planetary gears 4, a drive shaft 5 having a planetary gear holding portion 50 formed at one end, and a center case 12 and a plate 13 that accommodate these components. It consists of

The internal gear 2 is a substantially hollow cylindrical gear member having internal teeth formed all around the inner peripheral surface 21, and is rotatably held in the center case 12.
The internal gear 2 is regulated in a predetermined range by a plate 13 for a rearward (rightward in the figure) displacement and a forward (leftward in the figure) displacement by a spring 8. The sun gear 3 is an external tooth formed near the front end of the motor shaft 33, and is supported coaxially with the internal gear 2 through a bearing 34 fitted in a shaft hole at the rear end of the drive shaft 5. Has been done.

A plurality of planetary gears 4 are arranged at equal intervals on the circumference, and the inner teeth 2 of the internal gear 2 are arranged on the outer side.
1, the inner gear meshes with the outer teeth of the sun gear 3 and is driven by the sun gear 3. All the planetary gears 4 are rotatably supported by a planetary gear holding portion 50 formed at the rear end of the drive shaft 5 via a hollow cylindrical bearing 40. The planetary gear holding portion 50 is fixed to the flange portion 51 formed as a part of the drive shaft 5 and a through hole provided in the flange portion 51 in parallel with the axis of the drive shaft 5 by an interference fit. It is composed of a planetary gear shaft 52. The planetary gear 4 can rotate around the planetary gear shaft 52 and can also revolve along with the rotation of the drive shaft 5 together with the planetary gear shaft 52.

The fitting depth of the drive shaft 5 and the motor shaft 33 is regulated by the washer 35.
The rearward displacement of circlip 55
It is regulated by the thrust washer 56. Also,
The plate 13 also has a function of preventing the planetary gear 4 from coming off. In the planetary gear speed reduction mechanism 6 having the above configuration, even if the sun gear 3 formed on the outer periphery of the motor shaft 33 is driven by the motor 30 to rotate, the internal gear 2 held in the center case 12 has a predetermined shape. It does not rotate until the torque is exceeded. Therefore, the planetary gear 4 is sandwiched between the rotating sun gear 3 and the non-rotating internal gear 2 and meshes with both gears 2 and 3, so that the planetary gear 4 revolves in the rotation direction of the sun gear 3 while rotating. , Planetary gear holder 5
The drive shaft 5 is rotationally driven via 0. At that time, a torque that tries to rotate in a direction opposite to the rotation direction of the sun gear 3 and the drive shaft 5 is applied to the internal gear 2, and this torque is transmitted to the center case 12 via the spring 8.

(Embossed Surface and Spring of Embodiment 1) Now, among the constituent elements of the planetary gear reduction mechanism 6 described above, the outer peripheral portion of the front end surface 24 of the internal gear 2 is provided with unevenness in the circumferential direction. The uneven surface 7 is formed. on the other hand,
A spring 8 as a spring elastic member is fixed to the center case 12, and the spring 8 is in contact with the uneven surface 7 with a pressing force.

That is, the uneven surface 7 is, as shown in FIG.
It is formed of trapezoidal convex portions 75 and concave portions 76 that are alternately arranged, and is formed in order of a top surface 71, a downward slope 72, a bottom portion 73, and an upward slope 74. The spring 8 has a flat portion 81 formed in a flat shape near the tip.
An arm portion 82 supporting the flat surface portion 81, and a flat surface portion 81.
And a slanted surface portion 84 that is diagonally continuous. The slope portion 84 and the arm portion 82 are provided in a direction that does not oppose the normal displacement direction R due to the torque applied to the internal gear 2.

As shown in FIG. 4A, the spring 8 is a pressing member of a substantially ring-shaped leaf spring, and is equally spaced in the circumferential direction (every 60 °) from the outer periphery of the hollow disk-shaped ring portion 83.
The six arm portions 82 and the contact portion 81 (see FIG. 4B) are cut and raised. On the inner circumference of the ring portion 83,
Protrusions are formed at equal intervals in the circumferential direction in the center direction, and one screw hole 80 penetrates each of the protrusions. As shown in FIG. 2 again, the spring 8 is fixed to the center case 12 by the ring portion 83 by the screw 87 that penetrates the screw hole 80 and is fastened to the screw hole of the center case 12. Each of the three screws 87 is subjected to a retaining process.

The number of the irregularities formed on the irregular surface 7 is the number of the arm portions 82 of the spring 8 (six in this embodiment).
And are arranged at equal intervals in the circumferential direction. Therefore, the slope portion 84 of the six arms 82 of the spring 8 is
Both are in contact with the same slope or flat surface of the uneven surface 7, and evenly generate pressing force and friction torque. (Main Operational Effects of First Embodiment) Since the starter with the planetary gear speed reduction mechanism of the present embodiment is configured as described above,
It exerts excellent effects as follows.

That is, the uneven surface 7 of the internal gear 2
At the abutting portion of the spring 8 fixed to the center case 12, one of the following four states occurs depending on the magnitude and fluctuation range of the torque applied from the planetary gear 4 to the internal gear 2. In the following description, it will be easier to understand with reference to FIGS. 2 and 3. The first state is a no-load state. In this state, no torque is applied to the internal gear 2.
It is stable by abutting 2,74.

The second state is a normal load state. In this state, torque is applied to the internal gear 2 (indicated by R in FIG. 3 to indicate the rotation direction of the outer peripheral portion), but not as large as the meshing impact torque. Therefore, although the internal gear 2 rotates slightly, the convex portion 7 of the uneven surface 7
The ascending slope 74 forming 5 contacts the slope 84 of the spring 8, and the rotation of the internal gear 2 in the R direction stops. That is, in this state, the internal gear 2 does not rotate until the spring 8 climbs up the ascending slope 74 of the uneven surface 7 and exceeds the convex portion 75. That is, the internal gear 2 rotates only until the slope portion 84 of the spring 8 stops somewhere on the upward slope 74 of the uneven surface 7.

As a result, in this normal load state, the internal gear 2 does not continue to slide (rotate) with respect to the spring 8 fixed to the center case 12,
The internal gear 2 is stopped with respect to the drive housing 1. Therefore, in the above-described normal load state, the starter according to the present embodiment is similar to a normal starter with a planetary gear reduction mechanism in which the internal gear is fixed to the housing, and the planetary gear reduction mechanism 6 has a small loss in the motor shaft output. Is transmitted to the drive shaft 5 via.

The third state is an excessive load state. In this state, an excessive torque such as meshing impact torque is applied to the internal gear 2, and the slope portion 84 of the spring 8 climbs up the upward slope 74 of the uneven surface 7. Beyond the convex portion 75, the internal gear 2 overcomes the frictional force of the spring 8 and the component force of the pressing force and rotates in the R direction. Therefore, the excessive load torque applied to the internal gear 2 is absorbed by the rotation of the internal gear 2 and is not directly transmitted to the drive housing 1, so that it is applied to the planetary gear reduction mechanism 6. Impact load is relieved. Further, the impact torque transmitted to the sun gear 3 formed on the motor shaft (armature shaft) 33 is also reduced by the rotation of the internal gear 2.

Therefore, according to the present embodiment, it is possible to absorb impact loads such as meshing impacts, and it is not necessary to tighten the requirements for the strength of each constituent member.
It is possible to provide a lightweight, small-sized starter with a planetary gear speed reduction mechanism at low cost. When the overloaded state ends, the internal gear 2 quickly returns to the normal loaded state or the unloaded state where the internal gear 2 does not rotate.

The fourth state is a variable load state, in which the drive shaft 5 is rotated by the rotation of the crankshaft (not shown) of the engine (not shown).
The torque load on the load fluctuates, and the load value is not only a positive value but also a zero value or a negative value. In this state, the direction of the torque applied to the internal gear 2 changes due to the pulsating load, and the torque fluctuates similarly to the load, and intermittently takes zero or a negative value.

Then, the inclined surface portion 84 of the spring 8 moves up and down along the ascending inclined surface 74 of the uneven surface 7 in response to the varying torque, and permits the minute rotation of the internal gear 2. That is, the internal gear 2 reciprocates by rotating a relatively small rotation angle in response to torque fluctuation, and the spring 8
The fluctuating torque is absorbed by the elastic deformation of and the friction with the spring 8. The spring 8 in contact with the ascending slope 74 of the uneven surface 7 gives a predetermined torque to the internal gear 2 while going up and down the ascending slope 74 as the internal gear 2 rotates. Therefore, even if the load applied to the drive shaft 5 has a negative value intermittently, the gears 2, 3 and 4 of the planetary gear reduction mechanism 6 do not rattle due to the meshing of the gears. . Further, no impact due to play or the like generated in the fitting portion of the gears 2, 3, 4 with the shaft is generated.
As a result, in the starter with the planetary gear speed reduction mechanism of the present embodiment, the drive shaft 5 is driven by the high reduction ratio of the planetary gear speed reduction mechanism 6.
Despite the large equivalent moment of inertia at, the noise at the start due to backlash is prevented.

That is, according to this embodiment, the above-mentioned noise generation is prevented. As a result, the noise generated by the occupants and others around the engine at the time of starting the engine can be reduced as a whole. In order to confirm this effect, the inventors conducted a noise test in which a prototype starter with a planetary gear speed reduction mechanism of the present example was assembled in an automobile and the noise was measured by a microphone installed at a distance of about 1 m from the vehicle body when the engine was started. went. As a result, as shown in FIG. 5 (● indicates prior art, ○ indicates this embodiment), the noise level is reduced by several decibels over almost the entire audible frequency range, and the planetary gear reduction mechanism of this embodiment is attached. We were able to prove the effectiveness of the starter.

(Other Functions and Effects of Embodiment 1) In the starter with a planetary gear speed reduction mechanism according to this embodiment, the surface of the internal gear 2 facing the motor 30 or the rear surface, that is, the front end surface 2
An uneven surface 7 is formed on the surface 4, and the spring 8 is in contact with the uneven surface 7 from the front. Here, it is relatively easy to form the uneven surface 7 on the outer peripheral portion of the front end surface 24 when manufacturing the internal gear 2, and the internal gear 2 with the uneven surface 7 can be manufactured at low cost. Further, the spring 8 can be easily manufactured by stamping or pressing, and can be easily fixed to the center case 12. Further, in the process of assembly, when the internal gear 2 is inserted into the center case 12 to which the spring 8 is screwed, the spring 8 does not hinder the insertion of the internal gear 2, so that the assembly is easy. .

Therefore, according to the starter with the planetary gear speed reduction mechanism of the present embodiment, not only is it possible to alleviate the meshing impact and reduce the backlash noise, but it is also easy to manufacture and inexpensive to produce. There is also.
That is, according to the present embodiment, the starter with a planetary gear speed reduction mechanism can be provided at a lower cost than the starter with a planetary gear speed reduction mechanism according to the related art, which has a shock absorbing effect but does not reduce backlash noise. There is an effect that can be.

In addition, in this embodiment, the concave-convex surface 7 and the spring 8 are used for the internal gear 2 and the center case 12.
It fits in a narrow hollow cylindrical space between and. Therefore, the size of the drive housing 1 only slightly extends in the axial direction, and the diameter of the center case 12 and its peripheral members is not increased. Therefore, according to the present embodiment, there is also an effect that the increase in volume of the starter with the planetary gear speed reduction mechanism due to the formation of the uneven surface 7 and the equipment of the spring 8 is suppressed to the minimum.

Further, in the starter with a planetary gear speed reduction mechanism according to this embodiment, the spring 8 can be easily manufactured from a spring alloy plate material by a well-known processing method such as punching, punching, and bending. Further, since the spring 8 has a substantially ring shape and is disposed coaxially with the inner cylinder of the center case 12, the number of the arm portions 82 having the abutting portion 81 formed at the tip is six, but Since it is fixed to the center case 12 with half three screws 87, the number of assembling steps is small.

Further, in this embodiment, since the arm portions 82, which are the cut-and-raised portions of the spring 8, are arranged at equal intervals on the circumference, the pressing force applied to the internal gear 2 is substantially even around the axis. Become. Therefore, according to the present embodiment, since an unbalanced pressing force is not applied to the internal gear 2, there is also an effect that uneven wear of the internal gear 2 and the planet gears 4 does not occur.

(Modification 1 of Example 1) In Example 1,
As shown in FIG. 3, the concave-convex surface 7 on the front end surface of the internal gear 2 was composed of concave portions 76 and convex portions 75 having a trapezoidal cross section arranged alternately in the circumferential direction. Other uneven shapes may be provided. Therefore, in this modification, as shown in FIGS. 6A and 6B, the uneven surface 7 ′ of the outer peripheral portion of the front end surface 24 of the internal gear 2 ′ is formed only by the ascending slope 77 and the descending slope 78. are doing. Even in the modified mode in which the internal gear 2'having such a concavo-convex surface 7'is incorporated in the starter with the planetary gear reduction mechanism similar to that of the first embodiment, the same effect as that of the first embodiment can be obtained.

The ascending slope 77 and the descending slope 78 are
The plane does not have to have a constant inclination angle, and may have, for example, a sinusoidal shape. Alternatively, since it is not necessary that the ascending slope 77 and the descending slope 78 have the same slope, a modification in which the concavo-convex surface 7 is formed by, for example, sawtooth-shaped concavities and convexities is also possible. As the shape of the uneven surface 7 is changed in this manner, it is considered that there are some differences in characteristics. Therefore, the optimum uneven shape (and number) should be obtained from the viewpoints of function, cost, life, etc. by experiments. If it is possible, it is still preferable.

(Modification 2 of Embodiment 1) In Embodiment 1,
The spring 8 is formed in a ring shape around the drive shaft 5 as shown in FIGS. 4A and 4B again, but a spring elastic member having a different shape can also be used. For example, as shown in FIGS. 7 (a) to 7 (c), a modified mode having a spring 8'which is a punching member from a leaf spring having a single claw-shaped contact portion 81 'and an arm portion 82'. Is also possible. In this modification, the spring 8'is provided with a single screw (not shown) through the screw hole 80 '.
It is fixed to 2 '(not shown). Center case 1
On the rear surface of the 2'hollow disk, a ridge 1 is formed by stamping.
21 is formed to contact the spring 8 ′ from both sides in the circumferential direction to limit the rotational displacement of the spring 8 ′ around the screw hole 80 ′.

A single spring 8'is provided for the center case 1.
Even if it is fixed to 2 ', a plurality of center cases 12'
It may be fixed to. The shape of the concave-convex surface 7 of the internal gear 2 with which the spring 8 ′ abuts may be the shape of the first embodiment or the shape of the above-described modification 1. The means for fixing the springs 8 and 8'to the center case 12 can be selected from various means such as welding, fitting, and riveting, in addition to screw fixing.

(Modification 3 of Embodiment 1) As a means for strengthening the pressing force of the spring 8 on the uneven surface 7 and a means for reinforcing the noise reduction effect, as shown in FIG. A modification in which the rubber cushion 9 is sandwiched between the center cases 12 is also possible. In this modification, the cushion 9 uses the elastic force of rubber to cause the spring 8 to move.
Since the inclined surface portion 84 is pressed against the uneven surface 7 of the internal gear 2, the inclined surface portion 84 and the uneven surface 7 come into contact with each other with a pressing force larger than the spring elastic force of the spring 8. Therefore, even if the diameter of the internal gear 2 is small for the impact torque applied, a torque reaction force sufficient to stop the rotation of the internal gear 2 is generated between the inclined surface portion 84 and the uneven surface 7. Can be generated. Therefore, according to this modification, in addition to the effect of the first embodiment described above, there is an effect that even a small planetary gear speed reduction mechanism can obtain a sufficiently strong shock absorbing effect and a backlash noise reducing effect. .

Further, since the cushion 9 which is a rubber elastic member has a stronger impact absorbing action and damping action than the spring 8, the cushion 9 absorbs the vibrations of the spring 8 and the center case 12 to suppress the vibration. Exert. At the same time, the cushion 9 also has a function of absorbing noise in the center case 12. Therefore, according to this modification, there is an effect that noise and vibration at the time of starting are further reduced.

Although the cushion 9 is fitted between the center case 12 and the spring 8 in this modification, it may be fixed by an adhesive. Alternatively,
For the spring 8 ′ shown in the modified mode 2, a donut-shaped rubber cushion may be arranged along the inner peripheral surface of the outer cylinder of the center case 12. Further, the cushion 9 need not be a solid rubber elastic member, but may be a hollow rubber elastic member or a sponge-like rubber elastic member.

(Modification 4 of Embodiment 1) In this modification (not shown), contrary to the above-described Embodiment 1 (see FIG. 2), the uneven surface in which the unevenness is arranged in the circumferential direction is the center. It is formed in the case 12, and the spring 8 is fixed to the front end surface 24 of the internal gear 2. Therefore, when an excessive torque is applied to the internal gear 2, the spring 8 rotates together with the internal gear 2, while the center case 12 having the uneven surface does not rotate.

Also according to this modification, the same effect as that of the first embodiment can be obtained. Further, it is easy to form the uneven surface by pressing or the like in the manufacturing process of the center case 12, and the cost does not increase so much, so that there is a cost advantage. The method of fixing the spring 8 to the internal gear 2 may be selected from various fixing means such as screw fixing, welding and fitting.

Modifications corresponding to the modifications 1 to 3 with respect to the first embodiment are possible with respect to this modification, and the effects similar to these can be obtained. [Embodiment 2] (Structure of Embodiment 2) In a starter with a planetary gear speed reduction mechanism according to a second embodiment of the present invention, as shown in Fig. 9, a sun gear 3 and an internal gear 2 of a planetary gear speed reduction mechanism 6'are used. The configuration of the reduction gear portion including the planetary gears 4 and the drive shaft 5 is generally the same as that of the first embodiment. The difference from the first embodiment is that the internal gear 2 ″ forming the uneven surface 7 ″, The shapes are a spring 8 ″ and a cushion 9 ′ that come into contact with the uneven surface 7 ″ with a pressing force.

That is, the internal gear 2 ″ has a hollow cylindrical front end bulge 25 that projects forward from the middle of the front end face, and the outer peripheral surface of the front end bulge 25 has a circumferential direction. An uneven surface 7 ″ on which unevenness is provided is formed. On the other hand, the spring 8 ″ is the same as that of the first embodiment 8 in that it is fixed to the center case 12 with the screw 87,
The stamped shape and the press-molded shape are different from those of the spring 8 of the first embodiment. That is, in the spring 8 ″ of this embodiment, the arm portion 82 ″ stands up from the vicinity of the outer circumference, and the slope portion 84 ″ formed at the tip of the arm portion 82 ″.
Touches the uneven surface 7 ″ from the outer peripheral direction with a pressing force.

Here, a cushion 9 ', which is sandwiched between the outer peripheral surface of the inclined surface portion 84 "and the inner peripheral surface of the outer cylinder of the center case 12, is in contact. The cushion 9'is donut-shaped. The rubber elastic member, which presses and biases the inclined surface portion 84 ″ by the rubber elastic force. Therefore, the inclined surface portion 84 ″ of the spring 8 ″ is urged by the spring elastic force of the spring 8 ″ and the rubber elastic force of the cushion 9 ′ to contact the uneven surface 7 ″.

(Effects of Second Embodiment) Also in this embodiment, the effects equivalent to those of the first embodiment and its fourth modification can be obtained. Therefore, according to the starter with the planetary gear speed reduction mechanism of the present embodiment, while being less expensive than the product according to the prior art, the effect of mitigating the meshing impact and the effect of reducing the noise at start (especially backlash noise) are exhibited. To be done.

(Modifications of Embodiment 2) Various modifications corresponding to the modifications of Embodiment 1 are possible for this embodiment as well, and the corresponding effects can be obtained. In addition, the above-described second embodiment is considered to be a modification in which the uneven surface 7 of the first embodiment is moved, and the following modification is also possible in the same manner.

First, the outer peripheral surface 23 of the internal gear 2
A modified mode is possible in which a concavo-convex surface is formed (see FIG. 2) and a spring elastic member (spring) is fixed to the inner peripheral surface of the outer cylinder of the center case 12. In this modification, the diameter of the starter is somewhat larger, but there is an advantage that the uneven surface and the spring can be provided without extending the entire length of the starter.

Second, the rear end surface 22 of the internal gear 2
(See FIG. 2) An uneven surface is formed, and a spring elastic member (spring) is attached to the outer cylinder of the center case 12 or the plate 13.
Modifications of the configuration in which is fixed are also possible. This modification has an advantage that the uneven surface and the spring can be provided without expanding the diameter of the starter. Further, since the uneven surface and the spring can be accessed without removing the planetary gear 4 and the internal gear 2, there is an effect that maintainability is improved.

Thirdly, the through hole 20 of the internal gear 2
It is also possible to adopt a modified mode in which a concavo-convex surface is formed on the inner peripheral edge (see FIG. 2) forming the and the spring elastic member (spring) is fixed to the center case 12. This modification has an advantage that the uneven surface and the spring can be provided without expanding the diameter of the starter, and the entire structure can be made compact.

Fifth, in each of the above-described modifications, the uneven surface and the spring may be reversed to form the uneven surface on the center case 12 or the plate 13 and the spring may be fixed to the internal gear 2. Is. Also in this modification, the working effect equivalent to the modification 4 of the first embodiment can be obtained. [Embodiment 3] (Structure of Embodiment 3) A starter with a planetary gear speed reduction mechanism as Embodiment 3 of the present invention has substantially the same structure as that of Embodiment 1, but as shown in FIG. The internal gear 2A and the spring 8A are different from those of the first embodiment.

That is, in this embodiment, the uneven surface 7A formed on the inner peripheral surface of the outer cylinder of the center case 12 as a part of the housing and the uneven surface formed on the outer peripheral surface of the internal gear 2 are used. 7A 'face each other with the spring 8A interposed therebetween. The spring 8A is a corrugated plate made of a strip-shaped leaf spring material that is closed in the circumferential direction.
2A uneven surface 7A and internal gear 2A uneven surface 7
It is pressed and sandwiched in a substantially radial direction with A '. The spring 8A is wavy in the circumferential direction, and has a convex portion 85 and a concave portion 8
6 and 6 are formed in alternation.

The uneven surface 7A and the uneven surface 7A 'are formed with the same number of unevenness in the circumferential direction.
The number of waves of the spring 8A that is in contact with A'with a pressing force is also the same. (Operation and Effect of Embodiment 3) Therefore, the internal gear 2
When a torque is applied to A within a predetermined range, the spring 8A held between the internal gear 2A and the center case 12A elastically deforms, and the internal gear 2A rotates. If the torque does not exceed the predetermined value, the rotation of the internal gear 2A stops within a predetermined range, and when the torque decreases thereafter, the internal gear 2A restores. With this restoring torque, the same effect of reducing backlash noise as in the first embodiment can be obtained.

On the other hand, if the above torque exceeds a predetermined value, it is between the internal gear 2A and the spring 8A, or
Slip between the center case 12A and the spring 8A over the convex portion occurs, and the internal gear 2A rotates until an excessive torque is settled. Excessive torque is not transmitted to the center case 12A and the sun gear 3 while the internal gear 2A is rotating, so that the impact load such as the meshing impact is alleviated as in the first embodiment.

Therefore, according to the starter with the planetary gear speed reduction mechanism of the present embodiment, it is possible to obtain the same effect as that of the first embodiment even with a configuration different from that of the first embodiment. Also, unlike the first embodiment, since the spring 8A is not fixed,
There is no failure due to a joint failure, and the reliability is improved accordingly. Since the spring 8 and the screw 87 (see FIG. 2) of the first embodiment are not necessary in this embodiment, the accommodation space can be omitted, and the starter of this embodiment is the same as that of the first embodiment.
It is shortened in the axial direction more than anything.

(Modification of Third Embodiment) For this embodiment, a leaf spring material is provided between the front end face 24 of the internal gear 2 (see FIG. 2) and the hollow disk of the center case (not shown). It is possible to modify the configuration in which the ring-shaped corrugated plate spring made of is pressed and held. Here, the surface of the corrugated plate spring is corrugated in a predetermined number radially. An uneven surface 7 is formed on the front end surface 24 of the internal gear 2, and another uneven surface (not shown) is also formed on the hollow disk of the facing center case. The number of spring waves is the same.

As the corrugated plate spring rotates, the corrugated surface 7 is formed on the front end surface 24 of the internal gear 2 and another corrugated surface is formed on the hollow disk of the center case that faces the corrugated plate spring. It compresses with the surface and stores elastic energy. Therefore, when torque is applied to the internal gear 2 within a predetermined range, the corrugated plate spring sandwiched between the internal gear 2 and the center case elastically deforms, and the internal gear 2 rotates slightly. To do. If the torque does not exceed the predetermined value, the rotation of the internal gear 2 stops within a predetermined range, and when the torque decreases thereafter, the internal gear 2 restores. With this restoring torque, the effect of reducing backlash noise can be obtained as in the first and third embodiments.

On the other hand, if the torque exceeds a predetermined value, slipping beyond the convex portion occurs between the internal gear 2 and the corrugated plate spring or between the center case and the corrugated plate spring, and the internal gear 2 2 rotates until an excessive torque is settled. Excessive torque is not transmitted to the center case or the sun gear 3 (see FIG. 2) while the internal gear 2 is rotating, so that an impact load such as a meshing impact is generated as in the first and third embodiments. Will be alleviated.

Therefore, it is possible to obtain the same effects as those of the first and third embodiments by this modification which is slightly different in configuration from the third embodiment. Also, as in the third embodiment,
Since the corrugated plate spring is not fixed, there is no failure due to a joint failure and reliability is improved. In addition, unlike the third embodiment, since the outer peripheral portion of the center case has no unevenness, it is easy to install in the starter, and there is an advantage that the increase in the volume of the starter is small.

[Embodiment 4] (Structure of Embodiment 4) A starter with a planetary gear speed reduction mechanism as Embodiment 3 of the present invention is substantially the same as that of Embodiment 1 (Figs. 1 and 2).
See)). The difference from the first embodiment is that, as shown in FIG. 11, a center case 12B having an uneven surface 7B formed on the inner peripheral side of an outer cylinder and an uneven surface 7B 'on the outer peripheral surface.
Is a point having an internal gear 2B formed with. Furthermore, the difference from the third embodiment is that, instead of the corrugated plate-shaped spring 8A of the third embodiment, a plurality of rubber round bars 90, which are round bar-shaped rubber elastic bodies, are aligned in the axial direction with the drive shaft 5. That is, it is arranged and pressed and sandwiched by both the concavo-convex surfaces 7B and 7B '.

(Effects of Third Embodiment) As described above, in this embodiment, the rubber round bar 90 is sandwiched between the uneven surface 7B of the center case 12B and the uneven surface 7B 'of the internal gear 2B. There is. Therefore, while no torque is applied to the internal gear 2B, both the concave-convex surfaces 7B and 7B 'are stable due to the rubber elasticity of the rubber round bar 90 with the concave portions aligned with each other.

When a torque in a predetermined range is applied to the internal gear 2B, the internal gear 2B rotates slightly. At that time, the rubber round bar 90 is formed on both the concave and convex surfaces 7B and 7B.
It rolls while being in contact with B ', and is compressed between the slopes of the two concavo-convex surfaces 7B, 7B' facing each other, and a repulsive force is generated.
Due to the repulsive force, a counter torque that balances the torque applied to the internal gear 2B is generated between the center case 12B and the rubber round bar 90, and the torque and the counter torque balance to rotate the internal gear 2B. Will stop.

When the torque applied to the internal gear 2B fluctuates within a predetermined range, the equilibrium positions of the concave and convex surfaces 7B and 7B 'sandwiching the rubber round bar 90 change, and the internal gear 2B reciprocally rotates. To do. As a result, even if the torque applied to the internal gear 2B becomes loose, the rubber round bar 9
With the elastic repulsive force of 0, the tooth flanks of the gears are kept pressed against each other, and the occurrence of backlash noise is prevented.

The torque applied to the internal gear 2B is
When the anti-torque limit of the rubber round bar 90 is greater than the limit, the rubber round bar 90 rolls over the convex portions of both the concave and convex surfaces 7B and 7B ', and the internal gear 2B largely rotates or rotates and becomes excessive. Torque is released. As a result, it is possible to reduce the impact load applied to each part by an excessive impact torque such as a meshing impact and prevent the starter from being broken.

As described above, according to the starter with the planetary gear speed reduction mechanism in this embodiment, similar to each of the above-described embodiments, both the shock mitigation and the start-up noise reduction are achieved with a simple and inexpensive structure. can do. Further, in this embodiment, since the rubber round bar 90 only rolls on both the concavo-convex surfaces 7B, 7B ', the concavo-convex surfaces 7B, 7B' are hardly worn or worn, so that the life can be extended. is there. Further, for the same reason, frictional noise and impact noise are not generated on both the concave and convex surfaces 7B and 7B ', so that there is an effect that the noise during starting is further reduced.

(Modification of Embodiment 3) A modification in which the rubber round bar 90 (see FIG. 11) of Embodiment 3 described above is replaced with a pipe spring which is a pipe-shaped spring elastic body is also possible. It is possible to obtain an effect similar to. In this modification, a retainer may be used to keep the distance between the plurality of pipe springs at a predetermined distance, if necessary. Although various types of retainers can be considered, for example, as shown in FIG. 12, two ring members 98 coaxially arranged at a predetermined distance, and a plurality of ring members 98 connecting both ring members 98 at both ends are provided. A retainer 96 including the wire 97 can be used. The wire rods 97 are arranged at equal intervals on the circumferences of both ring members, and pipe springs (not shown) are passed through the wire rods 97 during the assembly process and held around the wire rods 97.

According to this modified embodiment, in addition to the above-described function and effect, there is also an effect that there is no concern that the pipe spring will come out of a predetermined position between the concave and convex surfaces 7B and 7B '.

[Brief description of drawings]

FIG. 1 is a partial half cross-sectional view showing the configuration of a starter as a first embodiment.

FIG. 2 is a partial half cross-sectional view showing the configuration of the main part of the starter according to the first embodiment.

FIG. 3 is an enlarged view of the contact portion between the internal gear and the spring according to the first embodiment.

FIG. 4 is an assembly view showing the shape of the spring of the first embodiment (a) a plan view (b) a partial side view

FIG. 5 is a graph showing the effect of starting noise reduction in Example 1.

FIG. 6 is an assembly view showing the shape of the internal gear according to the first modification of the first embodiment (a) a front view (b) a partial side view;

FIG. 7 is an assembly view showing a shape of a spring according to a second modification of the first embodiment (a) a plan view (b) a front view (c).
Side view

FIG. 8 is a partial half cross-sectional view showing the configuration of the main parts of the third modification of the first embodiment.

FIG. 9 is a partial half cross-sectional view showing the configuration of the starter main part of the second embodiment.

FIG. 10 is a partial cross-sectional view showing the shape of the main part of the starter of the third embodiment.

FIG. 11 is a partial cross-sectional view showing the shape of the main part of the starter of the fourth embodiment.

FIG. 12 is a perspective view showing the shape of a retainer of Modification 1 of Example 4.

[Explanation of symbols]

1: Drive housing 12, 12A, 12B: Center case (housing in the present invention together with 1) 121: Protrusion 13: Plate 2, 2 ', 2A, 2B: Internal gear 20: Through hole 21: Tooth surface ( Inner peripheral surface) 22: Rear end surface 23: Outer peripheral surface 24: Front end surface 25: Front end projecting part 3: Sun gear 30: Motor 31: Rotor 3
2: Stator 33: Motor shaft 35: Washer 36: Yoke 4: Planetary gear 40: Bearing 5: Drive shaft 50: Planetary gear holding part 51: Flange part 52: Planetary gear shaft 53: Clutch 54: Pinion gear 55: Circlip 56: Thrust washer 6, 6 ': Planetary gear reduction mechanism 7, 7'7A, 7A', 7B, 7B ': Rough surface 71: Top surface 72: Downward slope 73: Bottom surface 7
4: Upward slope 75: Convex part 76: Recessed part 77, 78: Slope surface 8, 8 ', 8 ", 8A: Spring elastic member (spring) 80, 80': Screw hole 81, 81 ', 81": Flat part 82 , 82 ', 82 ": arm part 83: ring part 8
4: Slope 85: Convex 86: Recess 87: Screw 9: Rubber elastic member (cushion) 90: Rubber round bar 92: Magnet switch 93: Drive lever 96: Retainer 97: Wire material 98: Ring member F: Flywheel R : Rotation direction

Claims (8)

[Claims] 1. A motor for generating a rotational force, a housing forming a machine frame of a starter, an internal gear rotatably held with respect to the housing, and a shaft supported coaxially with the internal gear. A sun gear rotationally driven by the motor, a plurality of planetary gears that mesh with the internal gear and the sun gear and are driven by the sun gear, and a planetary gear holding portion that rotatably supports the planetary gears. A starter having a planetary gear speed reduction mechanism that is formed at one end and to which torque is transmitted from the holding section, and a torque applied to the internal gear causes a torque to be applied to the housing below a predetermined initial torque. In the stationary engagement state where the internal gear is fixed, and when the torque exceeds a predetermined limit torque, When an overrunning state in which the rotation of the null gear is allowed and a torque larger than the initial torque and smaller than the limiting torque are input, the rotational angle displacement of the internal gear is allowed with respect to the housing according to the input torque. It has a holding state in any one of rotational displacement engagement states, and depending on a relative rotational angle position of the internal gear with respect to the housing, a static engagement state, a rotational displacement engagement state, a transit state, a rotational displacement engagement state. A starter with a planetary gear speed reduction mechanism that has a continuous and continuous holding state. 2. The stationary engagement state, the rotational displacement engagement state, and the overriding state include an uneven surface in which unevenness is formed in a circumferential direction on one of the housing and the internal gear, and the housing and The starter with a planetary gear speed reduction mechanism according to claim 1, wherein the starter with a planetary gear speed reduction mechanism is formed by a contact locking member that is fixed to the other of the internal gears and is in contact with the uneven surface with a pressing force. 3. The concavo-convex surface is formed on an end surface of the internal gear facing the motor, and the abutment locking member is a spring elastic member made of a leaf spring. The starter with a planetary gear speed reduction mechanism according to claim 2. 4. The abutment locking member comprises a ring-shaped leaf spring arranged around the drive shaft, and surrounds a plurality of cut-and-raised parts or convex-shaped parts abutting on the uneven surface. The starter with a planetary speed reduction mechanism according to claim 2, wherein the starters are provided at equal intervals. 5. The starter with a planetary gear speed reduction mechanism according to claim 2, further comprising a rubber elastic member that presses and biases the contact locking member against the uneven surface. 6. A motor for generating rotational power, a housing forming a machine frame of a starter, an internal gear rotatably held in the housing, and a coaxial shaft with the internal gear in the housing. And a sun gear that is rotatably driven by the motor, meshes with the internal gear and the sun gear,
A plurality of planetary gears driven by the sun gear and a planetary gear holding portion that rotatably holds the planetary gears are formed at one end, and the planetary gear holding portion is rotatably supported by the housing and torque from the holding portion. In a starter having a planetary gear speed reduction mechanism including: a drive shaft to which is transmitted, two concavo-convex surfaces in which concavities and convexities are formed in a circumferential direction on surfaces of the housing and the internal gear that face each other; A starter with a planetary gear speed reduction mechanism, comprising: an abutment locking member which is sandwiched between the uneven surfaces and which abuts on both the uneven surfaces with a pressing force. 7. The starter with a planetary gear speed reduction mechanism according to claim 6, wherein the abutment locking member is a ring-shaped corrugated plate made of a leaf spring. 8. One of the concave and convex surfaces is formed on the outer peripheral surface of the internal gear, and the other is formed on the inner wall surface of the housing facing the outer peripheral surface. 7. The starter with a planetary gear speed reduction mechanism according to claim 6, which is one of a round bar-shaped rubber elastic body and a pipe-shaped spring elastic body.