JP3640977B2 - Oblique contact ball bearing and starter bearing device using the same - Google Patents

Description

[0001]
[Industrial application fields]
The present invention relates to an oblique contact ball bearing and a starter bearing device using the same.
[0002]
[Prior art]
In order to start the engine, a starter that gives a rotational force to the engine is used. Generally, in a starter, the rotational force of a motor is transmitted to a clutch shaft through a reduction gear mechanism and a one-way clutch, and power is transmitted to an engine rotation shaft through an output shaft connected to the clutch shaft.
[0003]
Conventionally, a general deep groove ball bearing has been used as a bearing for supporting the clutch shaft (see Japanese Utility Model Publication No. 63-28882).
[0004]
[Problems to be solved by the invention]
By the way, normally, the time for which the starter operates to start the engine is about 1 second. For this reason, the accumulated use time of the starter when used for 10 years at a normal use frequency is at most about 100 hours.
In addition, even if the bearing accuracy is poor and causes noise due to some vibrations, the motor noise itself at the start of the starter itself is large. Compared with this, the noise due to the bearing accuracy can be almost ignored. Is on the level.
[0005]
From this point of view, the use of the above-mentioned general deep groove ball bearing as the bearing that supports the clutch shaft of the starter is excessive in terms of durability and accuracy.
On the other hand, even in applications other than the starter, it may be excessive quality to use a general deep groove ball bearing.
[0006]
Accordingly, a first object of the present invention is to provide an oblique contact ball bearing that has sufficient performance to realize predetermined use conditions and is inexpensive to manufacture.
A second object of the present invention is to provide a starter bearing device that has sufficient performance for a starter and is inexpensive to manufacture.
[0007]
[Means for Solving the Problems]
In order to achieve the first object, the oblique contact ball bearing according to claim 1 is:
An outer ring formed by pressing a cold-rolled steel plate or a carbon steel plate, and having a spherical portion for the ball raceway and a large-diameter cylindrical portion and a small-diameter cylindrical portion that are continuously provided on both sides thereof,
An inner ring formed by pressing a cold-rolled steel plate or a carbon steel plate and having a spherical portion for a ball race that faces the spherical portion of the outer ring, and a large-diameter cylindrical portion and a small-diameter cylindrical portion that are continuously provided on both sides thereof. When,
A flange-shaped first sealing portion that is bent at the end of the small-diameter cylindrical portion of the inner ring and is close to the end of the small-diameter cylindrical portion of the outer ring;
An annular second sealing portion that is press-fitted into the inner peripheral surface of the large-diameter cylindrical portion of the outer ring and close to the large-diameter cylindrical portion of the inner ring;
The small-diameter cylindrical portion of the outer ring has an abutting end surface for restricting the axial movement of the outer ring substantially perpendicular to the plate surface of the steel plate forming the outer ring, and the large-diameter cylindrical portion of the inner ring moves in the axial direction of the inner ring. It has an end face for abutment for regulating the surface substantially perpendicular to the plate surface of the steel plate forming the inner ring, and preload is applied through these end faces for abutment. To do.
[0008]
In order to achieve the second object, a starter bearing device according to claim 2 comprises:
In a starter bearing device that is provided in a starter that houses a clutch shaft in which a rotational force of a motor is transmitted only in one direction via a speed reduction mechanism, and that rotatably supports the clutch shaft with respect to the casing.
The oblique contact ball bearing according to claim 1, wherein an outer ring is fixed to the casing and an inner ring is fixed to the clutch shaft;
And a biasing means for preloading that biases one of the inner ring and the outer ring in the axial direction.
[0009]
[Action]
According to the configuration of the first aspect of the present invention, if the outer ring and the inner ring have cylindrical portions on both sides of the spherical portion as described above, these can be easily formed with a predetermined dimensional accuracy by press molding. In addition, it is possible to realize a bevel contact ball bearing that has sufficient performance to realize predetermined use conditions and that is inexpensive to manufacture. The grease normally filled between the inner ring and the outer ring tends to be concentrated on the inner peripheral surface of the large-diameter cylindrical portion of the outer ring by centrifugal force. Since the annular second sealing portion is press-fitted, the aggregated grease can be prevented from leaking to the outside. On the other hand, between the small diameter cylindrical portions on the side where the grease is not concentrated, the first sealing portion formed by bending at the end of the small diameter cylindrical portion of the inner ring is brought close to the end of the small diameter cylindrical portion of the outer ring. Sufficient sealing performance can be ensured.
[0010]
According to the configuration of the invention according to claim 2, there is provided a starter bearing device that has the same effect as that of the invention according to claim 1, and thus has sufficient performance for a starter and is inexpensive to manufacture. Can do. In addition, rattling in the axial direction of the ball can be prevented by preloading by the biasing means.
[0011]
【Example】
Embodiments will be described in detail below with reference to the accompanying drawings. In the following, left and right are left and right in the drawings.
FIG. 2 is a schematic cross-sectional view of a starter to which an oblique contact ball bearing according to an embodiment of the present invention is applied. With reference to the figure, the starter includes a DC motor 11, and the motor 11 generates a rotational force necessary for starting the engine. The motor 11 is housed in a metal casing 12 that covers the entire starter, and includes an armature 13. The armature 13 includes a rotating shaft 14, and the rotating shaft 14 is rotatably supported by bearings 151 and 152 with respect to the casing 12. The armature 13 is provided with a commutator 16 coaxially. The commutator 16 is in contact with a brush 17, and an excitation current is supplied to the armature coil wound around the armature 13 through the brush 17. A stator 19 around which a field coil 18 is wound at a small interval is installed on the outer periphery of the armature 13.
[0012]
The rotation on the driving side is transmitted to the clutch shaft 22 via the clutch roller 35, but the rotation of the clutch shaft 22 is not transmitted to the driving side.
The clutch shaft 22 is formed of a hollow cylindrical body, and the clutch shaft 22 is a pair of oblique contact ball bearings 50 and 60 (characterized in this embodiment) (the right oblique contact with respect to the left oblique contact ball bearing 50). The ball bearing 60 is formed in a smaller diameter.) And is rotatably supported by the casing 12.
[0013]
An output shaft 26 is fitted into the hollow portion of the clutch shaft 22. The output shaft 26 is coupled to the inner periphery of the hollow portion of the clutch shaft 22 by a helical spline 27. The output shaft 26 can move in the axial direction with respect to the clutch shaft 22, and the clutch shaft 22. And the output shaft 26 are configured to transmit a rotational force. Then, the pinion 28 is fitted to the output shaft 26 so as to rotate integrally, and a fitting position with respect to the output shaft 26 is defined by a spring 29. In addition, a spring 30 is provided for the output shaft 26 so that the retracted position of the output shaft 26 as shown in the figure is always set. When the key switch for starting the engine is operated by a plunger mechanism not shown in detail in the drawing, the pinion 28 is moved to the ring gear 31 by moving to the protruding position shown by the chain line position shown in the drawing against the spring 30. Make sure they are engaged. Although not shown in detail, the ring gear 31 is configured such that the rotational force is transmitted to the rotation shaft of the engine, and the rotation of the output shaft 26 is applied to the ring gear 31 in a state where the ring gear 31 is engaged with the pinion 28. Transmitted so that the engine is rotationally driven for starting.
[0014]
Referring to FIG. 1, each of the oblique contact ball bearings 50, 60 is formed continuously at an outer ring 51, an inner ring 52, a plurality of balls 53 interposed between both wheels 51, 52, and an end of the inner ring 52. The first sealing portion 54 and the second sealing portion 55 fixed to the inner peripheral surface of the outer ring 51 are provided. Each of the oblique contact ball bearings 50, 60 is a full ball bearing that does not use a cage.
The outer ring 51 includes a spherical portion 512 including the raceway surface 511 of the ball 53, and a large diameter cylindrical portion 513 and a small diameter cylindrical portion 514 that are continuously provided on both sides thereof, and is formed by press molding. . The inner ring 52 includes a spherical portion 522 including the raceway surface 521 of the ball 53, and a large diameter cylindrical portion 523 and a small diameter cylindrical portion 524 that are continuously provided on both sides thereof, and is formed by press molding. ing. The first sealing portion 54 is continuously bent at the end of the small diameter cylindrical portion 524 of the inner ring 52, and its end surface 541 is close to the inner peripheral surface of the end of the small diameter cylindrical portion 514 of the outer ring 51. A labyrinth seal is formed. The first sealing portion 54 also functions as a retaining stopper for the ball 53. The second sealing portion 55 has an annular shape with a U-shaped cross section, is press-fitted into the inner peripheral surface 513 a of the large-diameter cylindrical portion 513 of the outer ring 51, and is close to the large-diameter cylindrical portion 523 of the inner ring 52. The second sealing portion 55 is also formed by press molding. The inner and outer rings 52, 51 and the second sealing portion 55 are made of, for example, chromium molybdenum steel such as JIS standard SCM415, 420, case-hardened steel such as JIS standard SCr420 or SAE standard 5120, or cold rolled steel plate of JIS standard SPC system, SPB. A metal material such as a carbon steel plate is preferably used, and is subjected to a hardening treatment such as press molding, carburizing treatment or induction hardening treatment.
[0015]
The clutch shaft 22 has a large-diameter cylindrical portion 221 and small-diameter cylindrical portions 222 and 223 provided on both sides thereof. The inner ring 52 of the left contact ball bearing 50 is fitted to the small diameter cylindrical portion 222 of the clutch shaft 22 so as to be integrally rotatable, and the axial end surface of the inner ring 52 is the end surface of the large diameter cylindrical portion 221 of the clutch shaft 22. By abutting against 221a, the axial movement of the inner ring 52 relative to the clutch shaft 22 is restricted. On the other hand, the inner ring 52 of the right oblique contact ball bearing 60 is fitted to the small-diameter cylindrical portion 223 of the clutch shaft 22 so as to be integrally rotatable, and the axial end surface of the inner ring 52 on the large-diameter cylindrical portion 523 side is the clutch shaft 22. The axial movement of the inner ring 52 relative to the clutch shaft 22 is restricted by being abutted against the end surface 221b of the large-diameter cylindrical portion 221. The diameter of the outer peripheral surface of the large-diameter cylindrical portion 221 of the clutch shaft 22 is such that each end surface of the large-diameter cylindrical portion 221 substantially covers the gap formed by the second sealing portion 55 of each oblique contact ball bearing 50, 60. It is set to be able to do it, and the sealing performance is improved by the labyrinth effect.
[0016]
Further, the outer ring 51 of the left oblique contact ball bearing 50 is fitted to an inner peripheral surface of an annular groove 121 formed in the housing 12 so as to be integrally rotatable. An annular disc spring 56 as an urging means is interposed between the peripheral wall surface 121a of the annular groove 121 and the axial end surface of the outer ring 51 on the small diameter cylindrical portion 514 side. The disc spring 56 applies a preload by urging the outer ring 52 rightward in the drawing, and prevents the ball 53 from rattling. On the other hand, the outer ring 51 of the right contact ball bearing 60 is fitted in an annular groove 122 formed in the housing 12 and having a smaller diameter than the annular groove 121 so as to be integrally rotatable. And the axial end surface of the small-diameter cylindrical portion 51 4 side of the outer ring 51 by being abutted against the end surface 122a of the annular groove 122, axial movement is restricted relative to the housing 12 of the outer ring 51. The diameter of the inner peripheral edge of the peripheral wall surface 122a is set so that the inner peripheral edge can substantially cover the gap formed by the first sealing portion 54 of the right oblique contact ball bearing 60, and the labyrinth effect. This improves the sealing performance. Further, the inner diameter of the disc spring 56 is set so that the inner peripheral edge of the disc spring 56 can substantially cover the gap formed by the first sealing portion 54 of the right oblique contact ball bearing 60. This improves the sealing performance.
[0017]
According to the present embodiment, since the outer ring 51 and the inner ring 52 having the cylindrical portions 513, 514, 523, and 524 on both sides of the spherical portions 512 and 522 are formed, these can be easily formed with a predetermined dimensional accuracy by press molding. Therefore, it is possible to provide sufficient performance for the starter and to reduce the manufacturing cost.
[0018]
The grease normally filled between the inner ring 52 and the outer ring 51 tends to be concentrated on the inner peripheral surface of the large-diameter cylindrical portion 513 of the outer ring 51 by centrifugal force. Since the annular second sealing portion 55 is press-fitted into the surface, the aggregated grease can be prevented from leaking to the outside. On the other hand, between the small diameter cylindrical portions 514 and 524 on the side where the grease is not aggregated, sufficient sealing performance can be secured by the first sealing portion 54. Since the first sealing portion 54 can be press-molded integrally with the small diameter cylindrical portion 514 of the inner ring 52, the manufacturing cost can be further reduced. Further, since the second sealing portion 55 is also a press-molded product, the manufacturing cost can be further reduced. And since sufficient sealing performance is ensured by these sealing parts 54 and 55, sufficient durability of the bearing can be ensured from the viewpoint of grease retention. Moreover, since each sealing part 54 and 55 is comprised by the labyrinth by the housing 12, the clutch shaft 22, the disc spring 56, etc., said sealing property can be improved more.
[0019]
The present invention is not limited to the above embodiment, and various design changes can be made without changing the gist of the present invention, such as application of the present invention to bearings and bearing devices other than the starter. .
[0020]
【The invention's effect】
According to the first aspect of the present invention, since the outer ring and the inner ring have cylindrical portions on both sides of the spherical portion, these can be easily formed with a predetermined dimensional accuracy by press molding, It is possible to realize an oblique contact ball bearing that has sufficient performance to be realized and that is inexpensive to manufacture. The grease normally filled between the inner ring and the outer ring tends to be concentrated on the inner peripheral surface of the large-diameter cylindrical portion of the outer ring by centrifugal force. Since the annular second sealing portion is press-fitted, the aggregated grease can be prevented from leaking to the outside. On the other hand, between the small diameter cylindrical portions on the side where the grease is not concentrated, the first sealing portion formed by bending at the end of the small diameter cylindrical portion of the inner ring is brought close to the end of the small diameter cylindrical portion of the outer ring. Sufficient sealing performance can be ensured.
[0021]
According to the second aspect of the present invention, it is possible to realize a starter bearing device that has the same effect as the first aspect of the invention, and that has sufficient performance for a starter and that is inexpensive to manufacture. . In addition, rattling in the axial direction of the ball can be prevented by preloading by the biasing means.
[Brief description of the drawings]
FIG. 1 is a schematic sectional view of a starter bearing device according to an embodiment of the present invention.
FIG. 2 is a partial cross-sectional side view of a starter including the bearing device.
[Explanation of symbols]
51 outer ring 512 spherical part 513 large diameter cylindrical part 514 small diameter cylindrical part 52 inner ring 522 spherical part 523 large diameter cylindrical part 524 small diameter cylindrical part 53 ball 54 first sealing part 55 second sealing part 56 disc spring (biasing means)

Claims (2)

An outer ring formed by pressing a cold-rolled steel plate or a carbon steel plate, and having a spherical portion for the ball raceway and a large-diameter cylindrical portion and a small-diameter cylindrical portion that are continuously provided on both sides thereof,
An inner ring formed by pressing a cold-rolled steel plate or a carbon steel plate and having a spherical portion for a ball race that faces the spherical portion of the outer ring, and a large-diameter cylindrical portion and a small-diameter cylindrical portion that are continuously provided on both sides thereof. When,
A flange-shaped first sealing portion that is bent at the end of the small-diameter cylindrical portion of the inner ring and is close to the end of the small-diameter cylindrical portion of the outer ring;
An annular second sealing portion that is press-fitted into the inner peripheral surface of the large-diameter cylindrical portion of the outer ring and close to the large-diameter cylindrical portion of the inner ring;
The small-diameter cylindrical portion of the outer ring has an abutting end surface for restricting the axial movement of the outer ring substantially perpendicular to the plate surface of the steel plate forming the outer ring, and the large-diameter cylindrical portion of the inner ring moves in the axial direction of the inner ring. It has an end face for abutment for regulating the surface substantially perpendicular to the plate surface of the steel plate forming the inner ring, and preload is applied through these end faces for abutment. Oblique contact ball bearing. In a starter bearing device that is provided in a starter that houses a clutch shaft in which a rotational force of a motor is transmitted in only one direction via a speed reduction mechanism, and that rotatably supports the clutch shaft with respect to the casing.
The oblique contact ball bearing according to claim 1, wherein an outer ring is fixed to the casing and an inner ring is fixed to the clutch shaft;
And a biasing means for preloading that biases one of the inner ring and the outer ring in the axial direction.

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