SPECIFICATION
TITLE OF THE INVENTION
PULLEY APPARATUS
TECHNICAL FIELD
[0001] The present invention relates to a pulley apparatus such as guide
pulley or tension pulley that is assembled and used in a belt power train
mechanism such as a mechanism that drives an auxiliary machine like a
compressor used in the air-conditioner of an automobile by way of a
continuous pulley, or a mechanism that transmits rotation force between a
crank pulley that is fastened to the end section of a crankshaft and a cam
pulley that is fastened to the end section of a camshaft by way of a timing
belt.
BACKGROUND ART
[0002] As a pulley apparatus such as a guide pulley or tension pulley that
is assembled and used in a belt power train mechanism, pulley apparatuses
having a synthetic resin pulley fastened to the outer ring of a rolling bearing
made of a metal material such as bearing steel have been conventionally
used in order to reduce weight and cost. FIG. 9 illustrates a construction of
a pulley apparatus in which a synthetic resin pulley as disclosed in JP
10-122339 (A) is assembled. This pulley apparatus 1 is composed of a
pulley 2 made of synthetic resin and around which a belt is placed, and a
rolling bearing 3, which is a single-row deep-groove radial ball bearing for
supporting the pulley 2 so as to be able to freely rotate around a support
shaft or the like. The rolling bearing 3 comprises- an inner ring 5 having a
single-row inner ring raceway 4 formed around the outer circumferential
surface thereof; an outer ring 7 having a single-row outer ring raceway 6
formed around the inner circumferential surface thereof; and a plurality of
rolling elements that are located between the inner ring raceway 4 and the
outer ring raceway 6 so as to be able to roll freely. Moreover, a seal plate 9
is provided between the outer circumferential surface of both end section of

the inner ring 5 and the inner circumferential surface of both end sections of
the outer ring 7, and together with preventing grease that is filled in the
internal space where the rolling elements 8 are located from leaking to the
outside, prevents dust and the like from the outside getting into the internal
space. The pulley 2 is fastened around the outer circumferential surface of
the outer ring 7 of the rolling bearing 3 made in this way.
[0003] The pulley 2 has an inner-diameter side cylindrical section 10 and
an outer-diameter cylindrical section 11 that are concentric with each other.
The outer circumferential surface in the middle section of the inner-diameter
side cylindrical section 10 and the inner circumferential surface in the
middle section of the outer-diameter cylindrical section 11 are connected by a
circular ring shaped connecting section 12, and a plurality of reinforcement
ribs 13 are provided on each of both sides of the connecting section 12 in a
radial shape. This kind of pulley 2 is such that the inner-diameter
cylindrical section 10 is provided and fastened around the outer ring 7 of the
rolling bearing 3 by injection molding. In other words, the pulley apparatus
1 is obtained by injecting molten thermoplastic resin inside a cavity having
an inner shape that corresponds to the outer shape of the pulley 2 which is
formed in a die with the portion near the outer circumference of the outer
ring 7 molded on the inner circumference side thereof, and after this
thermoplastic resin has cooled and solidified, opening the die and taking the
pulley 2 with the rolling bearing 3 from the cavity.
[0004] The pulley apparatus 1 that is constructed in this way is used as a
guide pulley or tension pulley which is assembled in belt power train
mechanism that drives an auxiliary machine of an automobile. In other
words, the inner ring 5 of the rolling bearing 3 is fitted and fastened onto a
support shaft that is fastened to a stationary portion of the engine such as
the cylinder block. A continuous belt is placed around the outer
circumferential surface of the pulley 2. As this continuous belt moves, the
pulley 2 rotates, and the contact angle and tension of the continuous belt is
maintained.
[0005] In the case of a pulley apparatus 1 in which a synthetic resin pulley
2 is fastened to the outer circumferential surface of the outer ring 7, the

outer ring 7 is made using metal plate such as bearing steel, so the
coefficient of linear expansion of the outer ring 7 and the pulley 2 are
different. Therefore, as the temperature rises during use, the adhesion
between the outer ring 7 and the pulley 2 decreases, and there is a possibility
that relative slipping (creep) will occur between the outer ring 7 and the
pulley 2. Technology for preventing this kind of creep is disclosed in JP
61-38218 (A), JP 50-20043 (U), JP 50-23540 (U), and JP 11-148550 (A). In
the pulley apparatus disclosed in JP 61-38218 (A), as illustrated in FIGS.
10A, 10B, knurling (serration) 14 is formed around the entire outer
circumferential surface of the outer ring 7a, and when a synthetic resin
pulley is fitted around the outside of the outer ring 7a, the knurling 14 bites
into the inner circumferential surface of the pulley, which prevents creep.
[0006] Moreover, in the pulley apparatus disclosed in JP 50-20043 (U), as
illustrated in FIGS. 11A, 11B, a concave groove 15a (15b) having differing
width along the axial direction is formed in the circumferential direction in
the outer circumferential surface of the outer ring 7b (7c), and a synthetic
resin pulley is fastened to the outer circumferential surface of the outer ring
7b (7c) by injection molding. When performing injection molding, molten
thermoplastic synthetic resin is filled into the concave groove 15a (15b).
The concave groove 15a has differing width in the axial direction in the
circumferential direction, so the inside surface of the concave groove 15a
(15b) engages with the synthetic resin that is solidified inside the concave
groove 15a (15b), which prevent the occurrence of creep between the outer
ring 7b (7c) and the pulley.
[0007] Furthermore, in the pulley apparatus disclosed in JP 50-23540 (U),
as illustrated in FIG. 12, a pair of concave grooves 15c are formed around the
entire outer circumferential surface of the outer ring 7d so as to be inclined
with respect to the axial direction and not parallel with each other, and a
synthetic resin pulley is fastened on the outer circumferential surface of the
outer ring 7d by injection molding. The pair of concave grooves 15c is
inclined in the axial direction, so the occurrence of creep between the outer
ring 7d and the pulley is prevented. In this construction, by making
direction of inclination of the pair of concave grooves 15c opposite from each

other, the axial loads that occur as the pulley rotates cancel each other out,
and thus a moment load that causes pulley apparatus to twist does not occur
in the outer ring 7d.
[0008] In the construction disclosed in JP 61-38218 (A), JP 50-20043 (U)
and JP 50-23540 (U), it is possible to prevent the occurrence of creep between
the pulley and the outer ring 7a to 7d, however, there is still some unsolved
problems. In other words, in the case of the construction disclosed in JP
61-38218 (A), knurling 14 is formed around the entire outer circumferential
surface of the outer ring 7a, so when performing heat treatment after the
knurling 14 is formed, there is a possibility that the outer ring 7a may
deform due to residual strain. Moreover, when forming an outer ring
raceway 6 around the inner circumferential surface of the outer ring 7a, it is
difficult to hold the outer circumferential surface of the outer ring 7a with
good precision. Therefore, there is a possibility that the workability and
processing precision of the outer ring raceway 6 will decrease.
[0009] On the other hand, in the case of the construction disclosed in JP
50-20043 (U) and JP 50-23540 (U), a cylindrical surface remains on the outer
circumferential surface of the outer ring 7b to 7d, so there is no decrease in
the workability or processing precision of the outer ring raceway 6.
However, as the performance of automobiles has increased in recent years,
there is a tendency for the tension in the belt placed around the pulley and
the rotational speed of the pulley to increase, and so there is increase in the
force that causes creep to occur between the pulley and the outer ring. In
the case where the force that causes creep is large, in the construction
disclosed in JP 50-20043 (U), it is necessary to make the difference in the
width dimension in the axial direction of the concave groove 15a (15b) large,
and in the construction disclosed in JP 50-23540 (U), it is necessary to make
the inclination angle of the concave grooves 15c large. When the difference
in the width dimension of the concave groove 15a (15b) or the inclination
angle of the concave grooves 15c is large, the processing area on the outer
circumferential surface of the outer ring 7b to 7d becomes large.
[0010] Furthermore, in the case of the construction disclosed in JP
50-20043 (U) and JP 50-23540 (U), the shape in the width direction of the

cylindrical surface that remains on the outer circumferential surface of the
outer ring 7b to 7d changes in the circumferential direction. Therefore,
when performing heat treatment of the outer ring 7b to 7d after the concave
grooves 15a to 15c have been formed, there is a possibility that the outer ring
7b to 7d will deform due to residual strain.
[0011] FIG. 13 and FIG. 14 illustrate construction that is disclosed in JP
11-148550 (A). In this construction, a locking groove 16 is formed in part in
the axial direction of the outer circumferential surface of the outer ring 7e of
the rolling bearing 3a, and a straight pattern knurling 19 is formed by
arranging concave sections 17 and convex section 18 alternately around the
entire circumference of the bottom surface of the locking groove 16 using
knurling process. Part of the synthetic resin of the pulley 2a is allowed to
enter into the concave sections 17 that are formed in the bottom surface of
the locking groove 16 of the outer ring 7e to form protrusions 20 that are long
in the axial direction on the inner circumferential surface of the pulley 2a.
The engagement between these protrusions 20 and the knurling 19 on the
outer ring 7e prevents the occurrence of creep between the pulley 2a and the
outer ring 7e.
[0012] In the case of the construction disclosed in JP 11-148550 (A), the
shape in the width direction of the cylindrical surface remaining on the outer
circumferential surface of the outer ring 7e is the same in the
circumferential direction, so even when performing heat treatment after the
knurling 19 has been formed on the outer circumferential surface of the
outer ring 7e, deformation of the outer ring 7e due to residual strain is
prevented. However, in this construction the number, shape and
dimensions of the concave sections 17 and convex sections 18 of the knurling
19 are not particularly regulated. Therefore, when the length in the
circumferential direction of the bottom surface of the concave sections 17 is
too short, or when the depth in the radial direction of the concave sections 17
is too deep, the part of the synthetic resin of the pulley 2a does not enter into
all of the concave sections 17, so there is a possibility that gaps (voids) will
occur between the inner circumferential surface of the pulley 2a and the
outer circumferential surface of the outer ring 7e. Particularly, when the

length in the circumferential direction of the concave sections 17 is short
(essentially 0), and the cross-sectional shape of the protrusions 20 is
triangular, it becomes easy of gaps to occur between the inner
circumferential surface of the pulley 2a and the outer circumferential surface
of the outer ring 7e. As a result, there is a possibility of looseness between
the pulley 2a and the outer ring 7e, or a possibility that it will not be possible
to sufficiently maintain the connecting strength between the pulley 2a and
the outer ring 7e.
[Related Literature]
[Patent Literature]
[0013]
[Patent Literature l] JP 10-122339 (A)
[Patent Literature 2] JP 61-38218 (A)
[Patent Literature 3] JP 50-20043 (U)
[Patent Literature 4] JP 50-23540 (U)
[Patent Literature 5] JP11-148550 (A)
SUMMARY OF THE INVENTION
[Problem to be Solved by the Invention]
[0014] In consideration of the problems above, it is the object of the present
invention to provide a pulley apparatus that is able to surely prevent the
occurrence of creep between a pulley made of synthetic resin and an outer
ring made of a metal material.
[Means for Solving the Problems]
[0015] The pulley apparatus of a first aspect of the present invention
comprises a pulley and a rolling bearing. The rolling bearing has an inner
ring that has an inner ring raceway around the outer circumferential surface
thereof, an outer ring that has an outer ring raceway around the inner
circumferential surface thereof, and a plurality of rolling elements that are
provided between the inner ring raceway and the outer ring raceway. The

pulley has an outer circumferential surface around which a belt is placed,
and an inner circumferential surface that is fitted around the outer
circumferential surface of the outer ring. The present invention can be
suitably applied to a pulley apparatus in which the inner ring raceway and
outer ring raceway are both single-row deep-groove type, and the rolling
elements are balls.
[0016] Particularly, in the pulley apparatus of this first aspect of the
present invention, at least one locking groove is provided around part in the
axial direction of the outer circumferential surface of the outer ring, the
locking groove having a width that is within the range of 1/20 to 1/2 the
width of the outer ring, and knurling is formed on the bottom surface of this
locking groove by a knurling process such that concave sections and convex
sections that extend in the width direction are alternately arranged around
the entire circumference. The number, shape and the dimensions of these
concave sections and convex sections are regulated so as to satisfy all of the
conditions (1) to (3) below.
[0017]
(1) Of these concave sections, the angle 0 of intersection between the
two inside surfaces that are on both sides in the circumferential direction of
the bottom surface and continuous with the tip end surfaces of the adjacent
convex sections is within the range 45° to 120°; these concave sections
having a trapezoidal shape.
(2) The diameter D of the circumscribed circle of the tip end surface
of the convex section and the length L in the circumferential direction of the
bottom surface of the concave sections satisfy the relationship 0.01D < L <
0.03D.
(3) The above diameter D and the depth h in the radial direction of
the concave sections satisfy the relationship 0.004D < h < 0.015D.
[0018] A plurality of trapezoidal shaped protrusions that extend in the
width direction and that engage with the concave sections are formed around
part in the axial direction of the inner circumferential surface of the pulley,
so that the pulley is supported by the outer circumferential surface of the
rolling bearing.

[0019] Preferably, the pulley is fastened to the outer circumferential
surface of the outer ring by injection molding, and the protrusions are
formed at the same time as this injection molding by molten resin of the
pulley being filled in the locking groove and hardening, with these
protrusions engaging with the concave sections.
[0020] Preferably, the concave sections and convex sections of the knurling
are provided so as to be inclined with respect to the axial direction.
[0021] The pulley apparatus of a second aspect of the present invention
also comprises: a rolling bearing having an inner ring that has an inner ring
raceway around the outer circumferential surface thereof, an outer ring that
has an outer ring raceway around the inner circumferential surface thereof,
and a plurality of rolling elements that are provided between the inner ring
raceway and the outer ring raceway; and a pulley that has an outer
circumferential surface around which a belt is placed, and an inner
circumferential surface that is fitted around the outer circumferential
surface of the outer ring.
[0022] At least one locking groove is provided around part in the axial
direction of the outer circumferential surface of the outer ring, the locking
groove having a width that is within the range of 1/20 to 1/2 the width of the
outer ring; and knurling is formed on the bottom surface of this locking
groove by a knurling process such that concave sections and convex sections
that extend in the width direction and in an inclined state with respect to the
axial direction are alternately arranged around the entire circumference;
each of these concave sections comprising a bottom surface and two inside
surfaces on both sides in the circumferential direction of the bottom surface
and that are continuous with the tip end surfaces of the adjacent convex
sections; these concave sections having a trapezoidal shape. Furthermore,
a plurality of trapezoidal shaped protrusions that extend in the width
direction and in an inclined state with respect to the axial direction and that
engage with the concave sections are formed in part in the axial direction of
the inner circumferential surface of the pulley.
[0023] Preferably in this aspect as well, the pulley is fastened to the outer
circumferential surface of the outer ring by injection molding, and the

protrusions are formed at the same time as this injection molding by molten
resin of the pulley being filled in the locking groove and hardening.
[0024] Preferably, locking grooves are formed in two locations in the axial
direction of the outer circumferential surface of the outer ring; and the
concave sections and convex sections of the knurling that is formed in the
bottom surfaces of these locking grooves are provided in a state so as to
incline at the same angle with respect to the axial direction in opposite
directions from each other.
[0025] It is also possible to apply the construction of the second aspect to
the construction of the first aspect. Moreover, it is also possible to apply the
conditions for the number, shape and dimensions of the concave sections and
the convex section of the first aspect to the construction of the second aspect.
[Effect of the Invention]
[0026] In the case of the pulley apparatus of the present invention, by
properly regulating the number, shape and dimensions of the concave
sections and convex sections of knurling that is formed around the outer
circumferential surface of the outer ring, it is possible to definitely prevent
the occurrence of creep between the pulley made of synthetic resin and the
outer ring made of a metal material.
[0027] Moreover, in a preferred embodiment of the present invention, it is
possible to keep the force that is applied to the areas of contact between the
surfaces on the sides in the circumferential direction of protrusions that are
formed around the inner circumferential surface of the pulley and the inside
surfaces of the knurling due to the rotation of the pulley small.
BRIEF DESCRIPTION OF THE DRAWINGS
[0028] FIG. 1 is a perspective view illustrating a rolling bearing that has
been removed from a pulley apparatus of a first example of an embodiment
of the present invention.
FIG. 2 is a front view as seen from the radial direction of the rolling
bearing in FIG. 1.
FIG. 3 is a partial cross-sectional view of section a-a in FIG. 2.

FIG. 4 is a drawing similar to FIG. 3 of a pulley apparatus of the
first example of an embodiment of the present invention, and illustrates the
state of a pulley fastened around the outer-diameter side of the outer ring,
FIG. 5 illustrates a second example of an embodiment of the present
invention, and is a partial cross-sectional perspective view of a pulley
apparatus.
FIG. 6 is a front view as seen from the radial direction of a rolling
bearing of a pulley apparatus of the second example of an embodiment of the
present invention.
FIG. 7 illustrates a third example of an embodiment of the present
invention, and is a partial cross-sectional perspective view of a pulley
apparatus.
FIG. 8 is a front view as seen from the radial direction of a rolling
bearing of a pulley apparatus of the third example of an embodiment of the
present invention.
FIG. 9 is a partial cross-sectional perspective view illustrating an
example of a conventional pulley apparatus.
FIGS. 10A and 10B illustrate a first example of construction for
preventing creep in a conventional pulley apparatus, where FIG. 10Ais a
partial cross-sectional view of a rolling bearing, and FIG. 10B is a side view
of a rolling bearing with part omitted.
FIG. 11A illustrates a second example and FIG. 11B illustrates a
third example of construction for preventing creep in a conventional pulley
apparatus.
FIG. 12 illustrates a fourth example of construction for preventing
creep in a conventional pulley apparatus, and is a front view of a rolling
bearing as seen from the outside in the radial direction.
FIG. 13 is a partial cross-sectional view that illustrates a fifth
example of construction for preventing creep in a conventional pulley
apparatus.
FIG. 14 is a cross-sectional view of section b-b in FIG. 13.
MODES FOR CARRYING OUT THE INVENTION

[0029]
[Example l]
FIG. 1 to FIG. 3 illustrate a first example of an embodiment of the
present invention. A feature of this example is the devising of the shape
and dimensions of concave sections 17a and convex sections 18a of knurling
19a that is formed on part of the outer circumferential surface of the outer
ring of a pulley apparatus that certainly prevents the occurrence of creep
between the pulley and outer ring. The construction and functions of the
other parts are the same as in a conventional pulley apparatus, so drawings
and explanations of identical parts are omitted or simplified, with the
explanation below centering on the features of this example.
[0030] The outer ring 7f of the rolling bearing 3b of the pulley apparatus of
this example has an outer diameter of 35 mm to 60 mm, a width dimension
of 8 mm to 20 mm, and a locking groove 16a is formed around part in the
axial direction of the outer circumferential surface. Concave sections 17a
and convex sections 18a are formed on the bottom surface of this locking
groove 16a so as to be alternately arranged around the entire circumference
to form knurling 19a. By filling part of synthetic resin of the pulley 2b into
the concave sections 17a and allowing the synthetic resin to solidify,
protrusions 20a that are long in the axial direction are formed in part in the
axial direction of the inner circumferential surface of the pulley 2b. By the
protrusion 20a engaging with the knurling 19a, the occurrence of creep
between the pulley 2b and the outer ring 7f is prevented. The width W19 of
the knurling 19a, and the width W7 of the outer ring 7f are set so as to be
regulated by the relationship 0.05W7 < W19 < 0.5W7. When W19 < 0.05W7,
there is a possibility that the creep torque that is applied between the pulley
2b and the outer ring 7f will not be able to be supported, which is undesirable.
On the other hand, when W19 > 0.5W7, it becomes difficult to form the
knurling 19a using knurling process.
[0031] The total number of concave sections 17a is taken to be 50 to 150.
When the number of concave sections 17a, or in other words, the number of
protrusions 20a is less than 50, the number of protrusions 20a becomes
insufficient, and there is a possibility that creep torque that is applied

between the pulley 2b and the outer ring 7f will not be able to be supported.
On the other hand, when the number of concave sections 17a exceeds 150,
there is a possibility that when trying to cause part of the synthetic resin of
the pulley 2b to penetrate, the synthetic resin will not spread out completely
in all of the concave sections 17a, and thus there is a possibility that gaps
will occur between the bottom surfaces 21 of the concave sections 17a and
the tip end surfaces of the protrusions 20a. Moreover, the length in the
circumferential direction of the protrusions 20a becomes short, and the
strength of the protrusions 20a will becomes low, so there is a possibility that
creep torque that is applied between the pulley 2b and the outer ring 7f will
not be able to be supported, and that durability of the pulley will not be able
to be maintained.
[0032] Moreover, inside surfaces (stepped surfaces) 23 that are continuous
with the tip end surfaces 22 of the convex sections 18a and that face each
other in the circumferential direction are provided on the inner surfaces of
the concave sections 17a, and the angle of intersection 9 between adjacent
inside surfaces 23 is regulated within the range of 45° to 120°. When the
angle of intersection 0 is less than 45°, there is a possibility that when trying
to cause part of the synthetic resin of the pulley 2b to penetrate, the
synthetic resin will not spread out completely in all of the concave sections
17a, and thus there is a possibility that gaps will occur between the bottom
surfaces 21 of the concave sections 17a and the tip end surfaces of the
protrusions 20a. On the other hand, when the angle of intersection 9
exceeds 120°, not only does it become difficult to sufficiently maintain the
number of concave sections 17a, but the pressure angle at the contact surface
between the inside surfaces 23 and the protrusions becomes small.
Therefore, it becomes easy for the inner circumferential surface of the pulley
2b to slide with respect to the outer circumferential surface of the outer ring
7f, and thus it is not possible to sufficiently obtain the effect of preventing
creep.
[0033] In addition, when the depth h in the radial direction of the concave
sections 17a, and the diameter D of the circumscribed circle of the tip end
surface of the convex sections 18a (diameter at the peak of the convex

sections 18a) are set so as to satisfy the relationship 0.004D < h < 0.015D.
When h > 0.015D, there is a possibility that when trying to cause part of the
synthetic resin of the pulley 2b to penetrate, the synthetic resin will not
spread out completely in all of the concave sections 17a, and thus there is a
possibility that gaps will occur between the bottom surfaces 21 of the concave
sections 17a and the tip end surfaces of the protrusions 20a. On the other
hand, when h < 0.004D, it is not possible to sufficiently maintain connecting
strength between the concave sections 17a and the protrusions 20a, and thus
there is a possibility that creep torque that is applied between the pulley 2b
and the outer ring 7f will not be able to be supported.
[0034] Furthermore, the length L in the circumferential direction of the
bottom surface 21 of the concave sections 17a, and the diameter D of the
circumscribed circle of the tip end surface 22 of the convex sections 18a are
set so as to satisfy the relationship 0.01D < L < 0.03D. When L < 0.01D, it
becomes difficult to sufficiently maintain the strength of the protrusions 20a,
and thus there is a possibility that the torque applied between the pulley 2b
and the outer ring 7f will not be able to be supported. On the other hand,
when L > 0.03D, it becomes difficult to sufficiently maintain the number of
concave sections 17a.
[0035]
[Example 2]
FIG. 5 and FIG.6 illustrate a second example of an embodiment of
the present invention. In this example, concave sections 17b and convex
sections 18b of knurling 19b are provided in an inclined state with respect to
the axial direction of a rolling bearing 3c. This kind of knurling 19b can be
formed by performing knurling on the bottoms surface of a locking groove
16b by a twill knurling tool. As in the first example of the embodiment,
part of the synthetic resin of the pulley 2c penetrates into the concave
sections 17b and solidifies to form protrusions 20b on the inner
circumferential surface of the pulley 2c that are inclined with respect to the
axial direction. The protrusions 20b engage with the knurling 19b on the
outer ring, which prevents the occurrence of creep between the pulley 2c and
the outer ring 7g.

[0036] In this example, the concave sections 17b and convex sections 18b
are provided in a state so as to be inclined with the axial direction of the
rolling bearing 3c, so as the pulley 2c rotates, it is possible to reduce the force
that is applied to the stepped surface of the knurling 19b from the side
surfaces in the circumferential direction of the protrusions 20b. The angle
(twist angle) a that is formed between the formation direction of the concave
sections 17b and the convex sections 18b and the axial direction of the rolling
bearing 3b is regulated within the range 0° < a < 10°, and preferably within
the range 0° < a < 3°. The lower limit value of the range for the twist angle
a is set from the aspect of keeping the force applied to the inside surface
(stepped surface) of the concave sections 17b from the side surfaces in the
circumferential direction of the protrusions small. On the other hand, the
upper limit value of the range for the twist angle a is set from the aspect of
preventing the force in the tangential direction with respect to the engaging
section between the side surfaces in the circumferential direction of the
protrusions 20b and the inside surfaces of the concave sections 17b from
becoming too large.
[0037] An axial load that occurs in the outer ring 7f as the pulley 2c rotates
is supported by the engagement between the end surfaces in the width
direction of the protrusions 20b and the inside end surfaces in the width
direction of the concave sections 17b. In this example, the inside end
surfaces in the width direction of the concave sections 17b are provided in a
perpendicular direction with respect to the axial direction of the outer ring 7f.
However, it is also possible to form the concave sections 17b so as to span
across the width direction of the locking groove 16b (in a state wherein both
end sections in the width direction of the concave sections 17b are open on
the surfaces of both sides in the width direction of the locking groove 16b), or
it is possible to form the inside end surfaces in the width direction of the
concave sections 17b as a surface that is orthogonal with respect to the
formation direction of the concave sections 17b and convex sections 18b.
The construction and effect of the other parts are the same as in the first
example of the embodiment. Preferably, in this example as well, the
conditions related to the number, shape and dimensions of the concave

sections and convex sections of the first example are applied.
[0038]
[Example 3]
FIG. 7 and FIG. 8 illustrate a third example of an embodiment of
the present invention. In this example, knurling 19b, 19c is formed at two
locations around the outer circumferential surface of the outer ring 7h so as
to be symmetrical about the center section in the axial direction of the outer
ring 7h. In other words, locking grooves 16b, 16c are formed at two
locations around the outer circumferential surface of the outer ring 7h that
are separated in the axial direction, and concave sections 17b, 17c and
convex sections 18b, 18c of the knurling 19b, 19c are formed in the bottom
surfaces of the locking grooves 16b, 16c so as to be inclined at the same angle
in opposite directions in the axial direction. However, the period (pitch) of
the concave sections 17b, 17c and convex sections 18b, 18c do not necessarily
need to be the same, and, for example, the period of the knurling 19c could be
shifted by half a period with respect to the period of the knurling 19b.
[0039] In this example, the knurling 19b, 19c are formed at two locations
on the outer circumferential surface of the outer ring 7h so as to be
symmetrical about the center section in the axial direction of the outer ring
7h. Therefore, the axial loads that occur in the outer ring 7h as the pulley
2d rotates can cancel each other out. The construction and effect of the
other parts are the same as in the second example of the embodiment.
[Specific Example]
[0040] Testing that was performed to confirm the effect of the invention
related to the first example of the embodiment above will be explained. In
this testing, a total of two kinds of samples of single-row deep-groove ball
bearings, having JIS bearing number 6203, with an inner diameter of 17 mm,
outer diameter of 40 mm and width of 12 mm, were formed such that one
kind of sample (example of the invention) that is within the technical scope
of the present invention, and the other kind of sample (comparative example)
is not within the scope of the present invention, and were such that the
number, shape and dimensions of concave sections and convex sections of the
formed knurling differed between each kind of sample. In each kind of

sample, the width dimension of the locking groove was 2.4 mm and the width
dimension of the knurling of both was 1.6 mm.
[0041]
[Table l]

[0042] In each of the examples illustrated in Table 1, the pulley
apparatuses are such that synthetic resin is injected into each of the outer
ring to form pulleys around the outer circumferential surface of the outer
rings. The synthetic resin material used for the pulleys was nylon 66, the
outer diameter dimension of the pulleys was 70 mm, and the width
dimension was 24 mm.
[0043] In the pulley apparatuses that were obtained in this way, pulleys
were fastened so as not to be able to rotate and a force in the rotation
direction was applied to the outer ring. In this state, the size of the torque
when creep (relative rotation of the outer ring with respect to the pulley)
occurred between the pulley and the outer ring was measured three times.
[0044]
[Table 2]

[0045] Table 2 illustrates the results of the test. The standard deviation

of the size of the torque when creep occurred was suppressed at 8.7 for the
example, which was about half of the 16.3 for the comparative example.
This shows that there are cases when the number, shape and dimension of
the knurling was not suitably regulated, gaps occurred between the bottom
surfaces of the concave sections of the knurling and the tip end surfaces of
the protrusions, and that it is not possible to sufficiently maintain the
connecting strength between the pulley and the outer ring. Moreover, it can
be seen that for the average value of the size of the torque when creep
occurred, there was about a 10% improvement in the case of the example of
the invention when compared with the comparison example. From the
testing above, it could be confirmed that there was definitely an
improvement in the size of the creep torque that could be supported between
the pulley and the outer ring by applying the present invention to the pulley
apparatus having construction, for example, as disclosed in JP 11-148550
(A).
[Explanation of Reference Numbers]
1 Pulley apparatus
2, 2a to 2d Pulley
3, 3a to 3c Rolling bearing

4 Inner ring raceway
5 Inner ring
6 Outer ring raceway
7, 7a to 7h Outer ring

8 Rolling body
9 Seal plate
10 Inner-diameter side cylindrical section
11 Outer-diameter side cylindrical section
12 Connecting section
13 Reinforcement rib
14 Knurling
15a to 15c Concave groove
16, 16a to 16c Locking groove

17, 17a to 17c Concave section
18, 18a to 18c Convex section
19, 19a to 19c Knurling
20, 20a, 20b Protrusion

21 Bottom surface
22 Tip end surface
23 Inside surface

CLAIMS
What is claimed is:
1. A pulley apparatus, comprising:
a rolling bearing having an inner ring that has an inner ring
raceway around the outer circumferential surface thereof, an outer ring that
has an outer ring raceway around the inner circumferential surface thereof,
and a plurality of rolling elements that are provided between the inner ring
raceway and the outer ring raceway; and
a pulley that has an outer circumferential surface around which a
belt is placed, and an inner circumferential surface that is fitted around the
outer circumferential surface of the outer ring; wherein
at least one locking groove is provided around part in the axial
direction of the outer circumferential surface of the outer ring, the locking
groove having a width that is within the range of 1/20 to 1/2 the width of the
outer ring;
knurling is formed on the bottom surface of this locking groove by a
knurling process such that concave sections and convex sections that extend
in the width direction of the knurling are alternately arranged around the
entire circumference; each of these concave sections comprising a bottom
surface and two inside surfaces on both sides in the circumferential direction
of the bottom surface and that are continuous with the tip end surfaces of the
adjacent convex sections; these concave sections having a trapezoidal shape
by regulating the angle of intersection between the inside surfaces within
the range 45° to 120°; and furthermore, the diameter D of the circumscribed
circle of the tip end surface of the convex section, the depth h in the radial
direction of the concave sections, and the length L in the circumferential
direction of the bottom surface of the concave sections satisfy the
relationship 0.004D ≤ h ≤ 0.015D, and 0.01D ≤ L ≤ 0.03D; and
a plurality of trapezoidal shaped protrusions that extend in the
width direction and that engage with the concave sections are formed around
part in the axial direction of the inner circumferential surface of the pulley.
2. The pulley apparatus according to claim 1, wherein

the pulley is fastened to the outer circumferential surface of the
outer ring by injection molding, and the protrusions are formed at the same
time as this injection molding by molten resin of the pulley being filled in the
locking groove and hardening.
3. The pulley apparatus according to claim 1, wherein
the concave sections and convex sections of the knurling are
provided so as to be inclined with respect to the axial direction.
4. A pulley apparatus, comprising:
a rolling bearing having an inner ring that has an inner ring
raceway around the outer circumferential surface thereof, an outer ring that
has an outer ring raceway around the inner circumferential surface thereof,
and a plurality of rolling elements that are provided between the inner ring
raceway and the outer ring raceway; and
a pulley that has an outer circumferential surface around which a
belt is placed, and an inner circumferential surface that is fitted around the
outer circumferential surface of the outer ring; wherein
at least one locking groove is provided around part in the axial
direction of the outer circumferential surface of the outer ring, the locking
groove having a width that is within the range of 1/20 to 1/2 the width of the
outer ring;
knurling is formed on the bottom surface of this locking groove by a
knurling process such that concave sections and convex sections that extend
in the width direction and in an inclined state with respect to the axial
direction are alternately arranged around the entire circumference; each of
these concave sections comprising a bottom surface and two inside surfaces
on both sides in the circumferential direction of the bottom surface and that
are continuous with the tip end surfaces of the adjacent convex sections;
these concave sections having a trapezoidal shape; and
a plurality of trapezoidal shaped protrusions that extend in the
width direction and in an inclined state with respect to the axial direction
and that engage with the concave sections are formed around part in the

axial direction of the inner circumferential surface of the pulley.
5. The pulley apparatus according to claim 4, wherein
the pulley is fastened to the outer circumferential surface of the
outer ring by injection molding, and the protrusions are formed at the. same
time as this injection molding by molten resin of the pulley being filled in the
locking groove and hardening.
6. The pulley apparatus according to claim 3 or claim 4, wherein
locking grooves are formed in two locations in the axial direction of
the outer circumferential surface of the outer ring; and the concave sections
and convex sections of the knurling that is formed in the bottom surfaces of
these locking grooves are provided in a state so as to incline at the same
angle with respect to the axial direction in opposite directions from each
other.