JP2005326000A - One-way clutch and clutch built-in type pulley device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a one-way clutch having engaging reliability during a low temperature and idling reliability during rotating an engine, and to provide a clutch built-in type pulley device. <P>SOLUTION: The one-way clutch comprises an inner ring having a cylindrical face on the outer peripheral face, an outer ring having a cam face on the inner peripheral face, a plurality of rollers arranged in wedge spaces formed between the cam face and the cylindrical face, and an elastic body for elastically thrusting the rollers in the engaging direction. Herein, a wedge angle, bearing pressure on a contact face during rotation, bearing pressure on the contact face during rest, and a PV value are set. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a one-way clutch and a pulley device with a built-in clutch, and more particularly to a one-way clutch and a pulley device with a built-in clutch that are used by being fixed to a rotating shaft of a starter motor that supplies power to a crankshaft of an engine.

  Conventionally, a motor pulley and a crank pulley are respectively arranged on the rotation shaft of the starter motor and the crankshaft of the engine, and an endless belt is stretched between the motor pulley and the crank pulley so that the rotational driving force of the starter motor is supplied to the engine. It is transmitted to the crankshaft. The motor pulley fixed to the rotation shaft of the starter motor is one-way that transmits the rotational driving force of the starter to the crankshaft of the engine when the engine is started and prevents the rotation of the engine from being transmitted to the starter after the engine is started. A clutch-equipped pulley apparatus incorporating a clutch is used (see, for example, Patent Document 1).

  One-way clutches used in pulley devices with built-in clutches for starters include a roller-type one-way clutch in which a roller is disposed between the inner ring cylindrical surface and the outer ring cam surface, or between the inner ring and outer ring cylindrical surfaces. There is a sprag type one-way clutch in which a sprag is arranged.

Specifically, in the roller-type one-way clutch, the roller moves in a wedge space formed between the cylindrical surface of the inner ring and the cam surface of the outer ring, so that it is switched between the engaged state and the idling state. Transmits and shuts off the rotational driving force of the motor. In the engaged state, the roller is bitten on the shallow side of the wedge space by the force received from the outer peripheral surface of the inner ring and the spring force of the spring that presses the roller in the engaging direction, and in the idle state, the outer peripheral surface of the inner ring The roller is displaced to the wide side of the wedge space against the spring force of the spring based on the force received from the spring.
JP 7-317807 A

  By the way, in a one-way clutch for a starter, the viscosity of grease filled inside the clutch increases at low temperatures, the oil film on the contact surface between the roller and the inner ring becomes thick, and the friction coefficient on the contact surface does not have an oil film. Or it becomes small compared with a thin case. For this reason, the roller slipped in the engaged state, and power transmission could not be performed, resulting in poor engagement. In particular, such a phenomenon is likely to occur when the wedge angle is large or when the spring force of the spring pressing the roller is small. Further, in the idling state after the engine is started, the inner ring and the roller slip, the contact surface of the inner ring and the roller is worn, and the seizure or the like progresses to impair the idling property.

  The present invention has been made in view of the above-described problems, and an object thereof is a one-way clutch and a clutch built-in type capable of improving the reliability of engagement at a low temperature and the reliability of idling at the time of engine rotation. A pulley device is provided. Another object of the present invention is to provide a clutch built-in pulley device that ensures the grease retention of a one-way clutch.

The above object of the present invention can be achieved by the following constitution.
(1) The one-way clutch of the present invention is disposed in an inner ring having a cylindrical surface on the outer peripheral surface, an outer ring having a cam surface on the inner peripheral surface, and each wedge space formed between the cam surface and the cylindrical surface. A plurality of rollers, and an elastic body that elastically presses the rollers in the engaging direction,
The wedge angle in the wedge space is 2α [°],
The surface pressure of the contact surface between the inner ring and the roller during rotation is P1: 2 × F1 / (π × b1 × L) [Pa],
The sliding speed of the contact surface is V: R1 × ω [m / sec],
The surface pressure of the contact surface at rest is P2: 2 × F2 / (π × b2 × L) [Pa],
When
P1 × V ≦ 700 × 10 ⁶ ,
P2 ≧ (0.0004 × (2α) ^3.6 ) × cos (θ + 2α) / (π × sin (2α) × b2 × L), and
2α> 4
One-way clutch characterized by being.
However,
F1: Load on the contact surface during rotation Fs × cos (θ + 2α) / sin (2α) −m × (R1 + R2) × ω ² [N]
F2: Load on the contact surface at rest Fs × cos (θ + 2α) / sin (2α) [N]
π: Pi ratio
L: Effective length of the contact surface of the roller (roller length-2 x chamfered portion) [m]
b1: Contact width of the contact surface of the roller during rotation (8 × F1 × R / (π × E × L)) ^1/2 [m]
b2: Contact width of the contact surface of the roller at rest (8 × F2 × R / (π × E × L)) ^1/2 [m]
Fs: Spring force at the set position [N]
m: Mass of the roller [kg]
θ: Angle in the direction in which the elastic body pushes [°]
ω: angular velocity of the outer ring ω = (Fs × cos (θ + 2α) / sin (2α) / (2 × m × (R1 + R2))) ^1/2 [rad / s]
R: Equivalent curvature of the roller and the inner ring R = 1 / (1 / R1 + 1 / R2) [m]
R1: Radius of curvature of inner ring raceway surface [m]
R2: Curvature radius of the roller [m]
E: Equivalent Young's modulus of the roller and the inner ring E = 2 / ((1−ν1 ² ) / E1 + (1−ν2 ² ) / E2) [Pa]
E1: Young's modulus of the inner ring [Pa]
E2: Young's modulus of the roller [Pa]
ν1: Poisson's ratio of the inner ring ν2: Poisson's ratio of the roller.
(2) A pulley device with a built-in clutch that is attached to a rotating shaft of an auxiliary machine for an automobile and is used by being laid over a belt that transmits power to and from a crank pulley. A directional clutch is incorporated.

(3) a sleeve;
A pulley disposed around the sleeve and concentrically with the sleeve;
Rotational force is transmitted between the sleeve and the pulley only when the sleeve and the pulley are arranged between the sleeve and the pulley and only one of the sleeve and the pulley tends to rotate relative to the other in a predetermined direction. A one-way clutch to
At least one support bearing that is disposed between the sleeve and the pulley at a side of the one-way clutch to allow relative rotation between the sleeve and the pulley;
It is arranged between the one-way clutch and the support bearing in the axial direction in contact with the bearing outer ring of the support bearing, and has an inner diameter that is smaller than the inner diameter of the outer ring of the one-way clutch and larger than the outer diameter of the inner ring. An annular member;
With
A clutch built-in type pulley apparatus, wherein an end of an axial end of an outer ring of the one-way clutch facing the annular member has substantially the same shape as an axial intermediate part of the outer ring.
(4) a sleeve;
A pulley disposed around the sleeve and concentrically with the sleeve;
Rotational force is transmitted between the sleeve and the pulley only when the sleeve and the pulley are arranged between the sleeve and the pulley and only one of the sleeve and the pulley tends to rotate relative to the other in a predetermined direction. A one-way clutch to
A pulley device with a built-in clutch comprising:
The outer ring of the one-way clutch has a flange portion formed integrally or separately on the outer side in the axial direction, and the flange portion has an inclined portion bent inward in the axial direction. Type pulley device.

  According to the one-way clutch and the pulley apparatus with a built-in clutch of the present invention, the wedge angle, the contact surface pressure at rest and the PV value are set so that the reliability of engagement at low temperature and the idling at engine rotation are set. Reliability can be improved.

  Hereinafter, a one-way clutch and a pulley device with a built-in clutch according to each embodiment of the present invention will be described in detail with reference to the drawings.

(First embodiment)
FIG. 1 is a longitudinal sectional view of a pulley device with a built-in clutch according to a first embodiment of the present invention, and FIG. 2 is a sectional view of a one-way clutch in FIG.

  As shown in FIG. 1, the pulley apparatus 10 with a built-in clutch is disposed between an engine crankshaft and a starter motor. The pulley device 10 with a built-in clutch includes a sleeve 11 that is fixed to a rotating shaft (not shown) of a starter motor, a radially outer side of the sleeve 11 that is concentric with the sleeve 11, and a belt groove 12 a that is provided on the outer peripheral surface. And a formed pulley 12. A driving belt (not shown) suspended from a crank pulley (not shown) fixed to the crankshaft of the engine is stretched over the belt groove 12a.

  Further, only when the sleeve 11 tends to rotate relative to the pulley 12 in a predetermined direction between the outer peripheral surface in the axially intermediate portion of the sleeve 11 and the inner peripheral surface in the axially intermediate portion of the pulley 12. A one-way clutch 13 for transmitting a rotational force between the sleeve 11 and the pulley 12 is disposed. A pair of support bearings 14a and 14b are arranged between the outer peripheral surface at both axial end portions of the sleeve 11 and the inner peripheral surface at both axial end portions of the pulley 12 so as to hold the one-way clutch 13 therebetween. . Deep groove ball bearings are used as the support bearings 14a and 14b, and support the sleeve 11 and the pulley 12 so as to be relatively rotatable while supporting a radial load applied to the pulley 12. In addition, in the outer peripheral surface of the sleeve 11, the axially intermediate portion is formed with a larger diameter than both axial end portions, and step surfaces 11a and 11b are formed therebetween.

  The support bearings 14a and 14b include a bearing inner ring 31 fitted on the outer peripheral surface of the axial end portion of the sleeve 11, a bearing outer ring 32 fitted on the inner peripheral surface of the axial end portion of the pulley 12, and a bearing inner ring. A plurality of balls 33 that are rolling elements disposed between both raceway surfaces of the bearing 31 and the bearing outer ring 32, and a cage 34 that holds the balls 33 in a rollable manner. The support bearings 14a and 14b are attached to both sides of the bearing outer ring 32 in the axial direction, and have a pair of seal members 35 and 36 that prevent foreign matter from entering from outside and leakage of lubricant such as grease from the inside. doing.

  As shown in FIGS. 1 and 2, the one-way clutch 13 is press-fitted and fixed to the outer peripheral surface of the sleeve 11 and is press-fitted and fixed to the inner peripheral surface 15 of the pulley 12 and the inner peripheral surface of the pulley 12. 15 has an outer ring 16 arranged concentrically with the inner ring 15. The inner peripheral surface of the outer ring 16 forms a cam surface having a plurality of concave portions 17 formed at equal intervals in the circumferential direction, and between the cylindrical surface 18 formed on the outer peripheral surface of the inner ring 15 and each concave portion 17. Are each formed with a uniform wedge space 19.

  A plurality of rollers 20 are rotatably provided in each wedge space 19 formed between the cylindrical surface 18 of the inner ring 15 and each concave portion 17 of the outer ring 16. The one-way clutch 13 is fixed to the outer ring 16 and rotates relative to the inner ring 15, and includes a cage 21 having a plurality of pockets for individually accommodating the rollers 20, and is secured to the cage 21. And a plurality of springs 22 that are elastic bodies that elastically press in the engagement direction.

  The outer ring 16 of the one-way clutch 13 has first and second flange portions 23 and 24 radially inward at both axial ends, and the inner peripheral end surfaces of the flange portions 23 and 24 are the outer periphery of the inner ring 15. Oppositely arranged close to the surface. As a result, the grease base oil filled between the inner peripheral surface of the outer ring 16 and the outer peripheral surface of the inner ring 15 allows the first and second flange portions 23 and 24 to be moved even when centrifugal force is applied. Movement to the support bearings 14a and 14b side is suppressed by the outer ring 16 having the grease, and the grease retaining property in the one-way clutch 13 can be maintained. In addition, the 2nd flange part 24 is formed by bending after incorporating the other structural member of the one-way clutch 13. As shown in FIG.

  Further, since the seal member 35 on the inner side in the axial direction of each support bearing 14a, 14b has a lip portion 35a that seals between the outer peripheral surface of the bearing inner ring 31, the grease base oil in the one-way clutch 13 is removed. Intrusion into the support bearings 14a and 14b is suppressed, and the grease retention in the one-way clutch 13 can be further improved.

  In the pulley device 10 with a built-in clutch configured in this way, when the engine is started, the rotational angular velocity of the rotation shaft of the starter motor is faster than the rotational angular velocity of the crankshaft of the engine. When the roller 20 tends to rotate relatively in the direction, the roller 20 is based on the force received from the outer peripheral surface of the inner ring 15 and the spring force of the spring 22, that is, the side where the recess 17 is shallow, that is, the width of the wedge space 19 is narrow. Each roller 20 engages between the inner ring 15 and the outer ring 16 in a wedge shape on the side. As a result, the pulley 12 and the sleeve 11 cannot be relatively rotated (engaged), and the rotational driving force of the starter motor is transmitted to the crankshaft. On the other hand, when the rotational angular velocity of the crankshaft becomes higher than the rotational angular velocity of the rotational shaft after the engine is started, the engagement of the roller 20 is released and the relative rotation between the pulley 12 and the sleeve 11 is free (in the idling state). Become.

In the pulley device 10 with a built-in clutch configured as described above, in order to obtain good engagement performance at low temperatures, the contact surface (initial contact) between the roller 20 and the inner ring 15 when the inner ring 15 is not rotating is stationary. Surface pressure P2: 2 × F2 / (π × b2 × L) [Pa] in the (surface) is set as shown in equation (1).
P2 ≧ (0.0004 × (2α) ^3.6 ) × cos (θ + 2α) / (π × sin (2α) × b2 × L) (1)

However,
F2: Contact surface load at rest Fs × cos (θ + 2α) / sin (2α) [N]
π: Pi ratio
L: Effective length of roller contact surface (roller length-2 x chamfered portion) [m]
b2: Contact width of roller contact surface at rest (8 × F2 × R / (π × E × L)) ^1/2 [m]
Fs: Spring force at the set position [N]
θ: Angle [°] in the direction in which the elastic body pushes against the tangential direction of the contact surface
R: Equivalent curvature of roller and inner ring R = 1 / (1 / R1 + 1 / R2) [m]
R1: Curvature radius of cylindrical surface [m]
R2: Roller radius of curvature [m]
E: Equivalent Young's modulus of roller and inner ring E = 2 / ((1−ν1 ² ) / E1 + (1−ν2 ² ) / E2) [Pa]
E1: Young's modulus of inner ring [Pa]
E2: Young's modulus of roller [Pa]
ν1: Poisson's ratio of inner ring ν2: Poisson's ratio of roller

  At low temperatures, the viscosity of the grease filled in the clutch increases, and the oil film between the contact surfaces of the roller 20 and the inner ring 15 becomes thick. For this reason, the friction coefficient at the contact surface between the roller 20 and the inner ring 15 becomes smaller than when there is no oil film or when the oil film is thin, and the roller 20 is poorly engaged. In particular, the larger the wedge angle 2α, the lower the surface pressure of the contact surface between the roller 20 and the inner ring 15, so that poor engagement tends to occur and a large coefficient of friction is required. Therefore, in order to obtain a required value of the friction coefficient on the contact surface, it was found that the surface pressure P2 of the initial contact surface at rest must satisfy the equation (1). Further, it can be seen from the formula (1) that the larger the wedge angle, the larger the surface pressure P2.

Further, in the pulley device 10 with a built-in clutch according to this embodiment, a PV value serving as an index of wear and seizure on the sliding contact surface is set in order to prevent wear on the contact surface between the roller 20 and the inner ring 15 during idling. Is done. In the roller type one-way clutch 13 as in the present embodiment, the sliding speed V: R1 × ω [m / sec] of the contact surface increases as the rotational speed increases (see FIG. 3A), and at the time of rotation. The contact surface pressure P1: 2 × F1 / (π × b1 × L) [Pa] decreases as the rotational speed increases because the centrifugal force acts on the roller 20 (see FIG. 3B). For this reason, the PV value has a maximum value (see FIG. 3C). Therefore, in order to reduce wear on the contact surface, the PV value is set so as to satisfy the following expression (2) by a wear experiment.
P1 × V ≦ 700 × 10 ⁶ (2)

However, in addition to the symbols described in equation (1),
F1: Load on the contact surface during rotation Fs × cos (θ + 2α) / sin (2α) −m × (R1 + R2) × ω ² [N]
b1: Contact width of the roller contact surface during rotation (8 x F1 x R / (π x E x L)) ^1/2 [m]
m: Roller mass [kg]
ω: angular velocity of outer ring ω = (Fs × cos (θ + 2α) / sin (2α) / (2 × m × (R1 + R2))) ^1/2 [rad / s]
And

Further, in the pulley device 10 with a built-in clutch according to the present embodiment, when the wedge angle 2α is too small, the roller 20 is not caught and released, so that a problem arises that the surface pressure becomes high and the idle rotation cannot occur. For this reason, the wedge angle 2α is set so as to satisfy the expression (3).
2α> 4 (3)

(Example)
Here, the roller diameter is 2.8 mm, the roller length is 12 mm, the effective length of the contact surface of the roller is 11.4 mm, the Young's modulus of the roller is 207 GPa, the Poisson's ratio of the roller is 0.3, the outer diameter of the inner ring is 35 mm, In the one-way clutch in which the Young's modulus of the inner ring is 207 GPa, the Poisson's ratio of the inner ring is 0.3, the angle θ in the direction of pushing the spring is 3.5 °, and the specific gravity of the roller is 7.8, FIG. The range of the wedge angle 2α and the spring force Fs satisfying the expressions 1) to (3) is shown. Therefore, by designing the one-way clutch of the present embodiment within the hatched range shown in FIG. 4, the clutch performance can be stabilized in the engaged state and the idling state.

  Therefore, according to this embodiment of the one-way clutch and the pulley device with a built-in clutch, the wedge angle, the contact surface pressure at rest, and the PV value are set as described above, so that the reliability of engagement at low temperatures can be achieved. And reliability of idling during engine rotation can be improved.

(Second Embodiment)
Next, a one-way clutch and a pulley device with a built-in clutch according to a second embodiment of the present invention will be described with reference to FIG. In addition, about the part equivalent to 1st Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  As in the first embodiment, the pulley device 40 with a built-in clutch according to the present embodiment is provided with a sleeve 11 fixed to the rotation shaft of the starter motor, and is disposed concentrically with the sleeve 11 on the radially outer side of the sleeve 11. Includes a pulley 41 having a belt groove 12a over which the belt is wound, a one-way clutch 42 and a pair of support bearings 14a and 14b disposed between the inner peripheral surface of the sleeve 11 and the outer peripheral surface of the pulley 41, and An annular member 43 is provided between the one-way clutch 42 and the one support bearing 14b.

  The inner peripheral surface of the pulley 41 is formed such that an axial intermediate portion where the one-way clutch 42 is disposed has a smaller diameter than both axial end portions where the pair of support bearings 14 are disposed, and a step surface 41a therebetween. , 41b are formed. The step surface 41 a of the pulley 41 is positioned substantially in the axial direction with the step surface 11 a formed on the outer peripheral surface of the sleeve 11, while the step surface 41 b is a step formed on the outer peripheral surface of the sleeve 11. It is located on the inner side in the axial direction with respect to the surface 11b.

  Further, the one-way clutch 42 of the present embodiment is different from that of the first embodiment in the shape of the outer ring 44 having the cam surface 17. That is, the outer ring 44 has a first flange portion 23 extending inward in the radial direction at one axial end portion, while a tip 45 of the other axial end portion has substantially the same shape as the axial intermediate portion. The other end side in the axial direction is opened.

  The annular member 43 disposed between the one-way clutch 42 and the support bearing 14b in the axial direction includes a rubber member 46 and a metal member 47 such as an iron washer as shown in FIG. The rubber member 46 is made of nitrile, polyacryl, silicon, fluorine, or the like. Further, the rubber member 46 and the metal member 47 may be provided as separate bodies or may be provided integrally. However, it is preferable that the rubber member 46 and the metal member 47 are integrally formed from the viewpoint of assembly. Examples of the annular member 43 in which the rubber member 46 and the metal member 47 are integrally provided include a metal gasket (“Soft Metal” manufactured by NOK Corporation), a graphite gasket (manufactured by Nippon Gasket Co., Ltd.), and the like.

  The annular member 43 is fitted and fixed to the inner peripheral surface of the pulley 41 by pressing the metal member 47 with the rubber member 46 facing the step surface 41 b when the support bearing 14 b is press-fitted into the pulley 41. As a result, the annular member 43 is in the axial direction between the one-way clutch 42 and the support bearing 14b, that is, with the stepped surface 41b of the pulley 41 and the sleeve, with the outer surface in contact with the bearing outer ring 32 of the support bearing 14b. 11 step surface 11b. The annular member 43 is smaller than the inner diameter of the outer ring 44 of the one-way clutch 42 and has an inner diameter greater than or equal to the outer diameter of the inner ring 15, and is arranged so that the inner peripheral end surface is in close proximity to the outer peripheral surface of the inner ring 15. Is done. Further, since the annular member 43 is provided so that the rubber member 46 is sandwiched between the step surface 41 b of the pulley 41 and the metal member 47, the step surface 41 b or inner peripheral surface of the pulley 41 and the metal member 47 are provided. Even if the inner side surface or the outer peripheral surface is formed to be somewhat rough, the rubber member 46 can be elastically deformed and brought into close contact with the stepped surface 41b to ensure the sealing performance between the pulley 41 and the annular member 43.

Therefore, according to the pulley device 40 with a built-in clutch of the present embodiment, the one-way clutch is disposed between the one-way clutch 42 and the support bearing 14b in the axial direction while being in contact with the bearing outer ring 32 of the support bearing 14b. An annular member 43 having an inner diameter smaller than the inner diameter of the outer ring 44 and equal to or larger than the outer diameter of the inner ring 15, and the tip 45 of the axial end of the outer ring 44 of the one-way clutch 42 is connected to the axial intermediate portion of the outer ring 44. It has substantially the same shape. As a result, the grease base oil filled between the inner peripheral surface of the outer ring 44 and the outer peripheral surface of the inner ring 15 of the one-way clutch 42 can be separated from the first flange portion 23 even when centrifugal force is applied. The annular member 43 is restrained from moving toward the support bearings 14a and 14b, and the grease retaining property in the one-way clutch 42 can be maintained. In addition, by providing the annular member 43, the one-way clutch 42 does not need to bend the end portion after the other components are incorporated into the outer ring 44, so that it is possible to improve the assembling property while maintaining the grease retaining property. Can do.
Other configurations and operations are the same as those in the first embodiment. Further, the outer ring 44 and the pulley 41 of the one-way clutch 42 may be integrally formed.

(Third embodiment)
Next, a one-way clutch and a pulley apparatus with a built-in clutch according to a third embodiment of the present invention will be described with reference to FIG. Note that portions equivalent to those of the second embodiment are denoted by the same reference numerals, and description thereof is omitted or simplified.

  In the clutch-equipped pulley device 50 according to the present embodiment, the outer ring 53 of the one-way clutch 52 has substantially the same shape as the axial intermediate portion over the distal ends 54 and 55 at both axial ends. The second embodiment differs from the second embodiment in that a pair of annular members 43 and 43 are respectively disposed between the one-way clutch 52 and the pair of support bearings 14a and 14b.

With the above configuration, the inner peripheral surface of the pulley 51 has both step surfaces 51 a and 51 b provided between the axial end portions and the axial intermediate portion having a smaller diameter than the axial end portions. Are formed so as to be positioned on the inner side in the axial direction with respect to the stepped surfaces 11a and 11b. As a result, the pair of annular members 43, 43 press the rubber member 46 toward the step surfaces 51a, 51b when the support bearings 14a, 14b are press-fitted into the pulleys, respectively. Each surface is fitted and fixed. As a result, the pair of annular members 43, 43 are in the axial direction between the one-way clutch 52 and the support bearings 14a, 14b, with their outer surfaces in contact with the bearing outer rings 32 of the support bearings 14a, 14b. Positioned between the step surfaces 51a and 51b of the pulley 51 and the step surfaces 11a and 11b of the sleeve 11, respectively.
Other configurations and operations are the same as those in the second embodiment. Further, the outer ring 44 and the pulley 41 of the one-way clutch 42 may be integrally formed.

(Fourth embodiment)
Next, a one-way clutch and a pulley device with a built-in clutch according to a fourth embodiment of the present invention will be described with reference to FIG. Note that portions equivalent to those of the second embodiment are denoted by the same reference numerals, and description thereof is omitted or simplified.

  In the clutch built-in pulley device 60 of the present embodiment, the inner peripheral surface of the pulley 61 has a single inner diameter in the axial direction. The annular member 64 differs from the annular member 43 of the second embodiment in that the rubber member 65 and the metal member 66 have substantially the same outer diameter as the inner diameter of the inner peripheral surface of the pulley 61.

  Further, in the one-way clutch 62, the inner ring 63 is formed thick with the outer peripheral surface being the cylindrical surface 18, and the outer ring 44 is the first extending inward in the radial direction at one axial end as in the second embodiment. One end 45 of the other axial end portion having the flange portion 23 has substantially the same shape as the axial intermediate portion and extends in the axial direction, with the other axial end side being open. The axial length of the outer ring 44 is shorter than the axial length of the inner ring 63 in consideration of the thickness of the annular member 64.

As in the second embodiment, the annular member 64 presses the metal member 66 toward the tip 45 at the other end in the axial direction of the outer ring 44 when the support bearing 14 b is press-fitted into the pulley 61, so that the pulley 61 It is fitted and fixed to the inner peripheral surface of. As a result, the annular member 64 has an outer surface that is in contact with the bearing outer ring 32 of the support bearing 14 b and an inner surface that is in contact with the tip 45 of the other end in the axial direction of the outer ring 44 of the one-way clutch 62. It is located between the direction clutch 62 and the support bearing 14b. The annular member 64 is provided so that the rubber member 65 is sandwiched between the tip 45 at the other axial end of the outer ring 44 and the metal member 66. It is possible to ensure tightness between the pulley 61 and the annular member 64 by closely contacting the peripheral surface.
Other configurations and operations are the same as those of the second embodiment.

(Fifth embodiment)
Next, a one-way clutch and a clutch-equipped pulley device according to a fifth embodiment of the invention will be described with reference to FIG. In addition, about the equivalent part to 3rd, 4th embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  In the pulley device 70 with a built-in clutch according to the present embodiment, as in the fourth embodiment, in the pulley 61 whose inner peripheral surface has a single inner diameter, the outer ring 53 of the one-way clutch 71 is connected to the tips 54 at both ends in the axial direction. 55 has substantially the same shape as the axially intermediate portion and is open on both sides in the axial direction. Between the one-way clutch 71 and the pair of support bearings 14a and 14b, a pair of annular members 64 and 64 is provided. Are different from the fourth embodiment in that they are respectively arranged.

With the above configuration, the axial length of the outer ring 53 is shorter than the axial length of the inner ring 63 in consideration of the thickness of the pair of annular members 64, 64. As a result, the pair of annular members 64, 64 press the metal member 66 toward the tips 54, 55 at both axial ends of the outer ring 53 when the support bearings 14a, 14b are press-fitted into the pulley 61, respectively. Thus, the pulley 61 is fitted and fixed to the inner peripheral surface of the pulley 61. As a result, the pair of annular members 64, 64 are respectively positioned between the one-way clutch 71 and the support bearings 14a, 14b in the axial direction with the outer surfaces thereof in contact with the bearing outer rings 32 of the support bearings 14a, 14b. Is done.
In addition, about another structure and effect | action, it is the same as that of the thing of 4th Embodiment.

(Sixth embodiment)
Next, a one-way clutch and a clutch-equipped pulley device according to a fifth embodiment of the invention will be described with reference to FIG. In addition, about the part equivalent to 3rd Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

The pulley apparatus with a built-in clutch 80 of this embodiment is different from that of the third embodiment in that the outer ring and the inner ring of the one-way clutch 83 are configured by the inner peripheral surface of the pulley 81 and the outer peripheral surface of the sleeve 82. That is, the cam surface 17 is formed on the inner peripheral surface in the axially intermediate portion of the pulley 81, and constitutes a wedge space together with the cylindrical surface 18 constituted by the outer peripheral surface of the axially intermediate portion of the sleeve 82.
Other configurations and operations are the same as those of the third embodiment.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.

  The first and second flange portions 23 and 24 and the annular members 43 and 64 of the outer ring of the one-way clutch in the above embodiment extend straight in the radial direction and are formed in a ring shape. For example, FIG. In the outer ring 16 having the first and second flange portions 23 and 24 shown, an inclined portion 92 that is bent linearly or curvedly inward in the axial direction from the base portion 90 or the intermediate portion 91 may be provided. . As a result, the grease base oil adhering to the flange portions 23, 24 or the inner peripheral ends of the annular members 43, 64 is released into the one-way clutch by centrifugal force, etc., so that the grease base oil moves to the support bearing side. It is suppressed and the grease retention can be further improved. In this case, the inclined portion 92 has a maximum inclination angle α of 5 ° or more, an axial width w from the proximal end portion to the distal end portion of the inclined portion 92 is 1 mm or more, and is provided on both axial sides of the outer ring. By satisfying at least one of the above, the grease retention can be further improved, and it is more preferable to satisfy all three. Moreover, when the inclined part 92 is provided in the axial direction both sides of an outer ring | wheel, the shape and structure of the inclined part 92 may each differ and be formed. When the inclined portion 92 is applied to the annular members 43 and 64 of the second to sixth embodiments, the inclined portion 92 is formed by bending the metal members 47 and 66.

  Note that at least one of the first and second flange portions 23 and 24 of the first embodiment may be provided separately from the outer ring 16 as shown in FIG. 12, and the flange formed as a separate body. The base portion 93 of the portion 23 may be sandwiched between the bearing outer ring 32 of the support bearing 14 a and the outer ring 16 of the one-way clutch 13. Further, as shown in FIGS. 12B and 12C, the base 93 may be bent or linearly bent and press-fitted into the inner peripheral surface of the pulley 12 alone. Similarly, the first flange portion 23 of the second and fourth embodiments may be provided separately from the outer ring 16.

  In the present invention, the support bearings disposed on both axial sides of the one-way clutch may be rolling bearings of a type other than the deep groove ball bearing. Moreover, in this embodiment, although a pair of support bearing is arrange | positioned at the axial direction both sides of a one-way clutch, at least 1 support bearing may be arrange | positioned at the axial direction one side.

  In addition, when the pulley device with a built-in one-way clutch is used for driving an auxiliary machine of an engine idle stop mechanism, an auxiliary machine such as a compressor is driven by a dedicated motor when the engine is stopped. Although it does not receive, it becomes the structure which receives the rotation fluctuation generate | occur | produced from the motor for an auxiliary machine drive.

  Further, in the pulley device with a built-in clutch in the second to sixth embodiments, it is optional to set the wedge angle, the contact surface pressure at rest and the PV value as in the first embodiment. By setting, the retention of grease can be improved, and at the same time, the reliability of engagement at a low temperature and the reliability of idling at the time of engine rotation can be improved.

  In addition, the pulley device with a built-in clutch in the second to sixth embodiments provides a rotational force between the sleeve and the pulley only when one of the sleeve and the pulley tends to rotate relative to the other in a predetermined direction. Any one-way clutch may be used, and the inner ring surface of the outer ring is a cylindrical surface and the outer ring surface of the inner ring is a cam surface. You may communicate.

It is a longitudinal cross-sectional view of the pulley apparatus with a built-in clutch in 1st Embodiment of this invention. It is a cross-sectional view of the one-way clutch in FIG. It is a figure for demonstrating the relationship between a rotation speed and PV value. It is a figure which shows the range of a wedge angle and a spring force of the pulley apparatus with a clutch in an Example. It is a longitudinal cross-sectional view of the pulley apparatus with a built-in clutch in 2nd Embodiment of this invention. It is a perspective view of the annular member of FIG. It is a longitudinal cross-sectional view of the pulley apparatus with a built-in clutch in 3rd Embodiment of this invention. It is a longitudinal cross-sectional view of the pulley apparatus with a built-in clutch in 4th Embodiment of this invention. It is a longitudinal cross-sectional view of the pulley apparatus with a built-in clutch in 5th Embodiment of this invention. It is a longitudinal cross-sectional view of the pulley apparatus with a built-in clutch in 6th Embodiment of this invention. It is sectional drawing of the modification of the flange part or annular member of the one-way clutch of this invention. It is sectional drawing of the other modification of the flange part or annular member of the one-way clutch of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 One-way clutch built-in pulley apparatus 11 Sleeve 12 Pulley 12a Belt groove 13 One-way clutch 14 Support bearing 15 Inner ring 16 Outer ring 17 Recessed part 18 Cylindrical surface 19 Wedge space 20 Roller 21 Cage 22 Spring (elastic body)

Claims (2)

An inner ring having a cylindrical surface on the outer peripheral surface, an outer ring having a cam surface on the inner peripheral surface, a plurality of rollers disposed in each wedge space formed between the cam surface and the cylindrical surface, and the rollers A one-way clutch provided with an elastic body that elastically presses in the opposite direction,
The wedge angle in the wedge space is 2α [°],
The surface pressure of the contact surface between the inner ring and the roller during rotation is P1: 2 × F1 / (π × b1 × L) [Pa],
The sliding speed of the contact surface is V: R1 × ω [m / sec],
The surface pressure of the contact surface at rest is P2: 2 × F2 / (π × b2 × L) [Pa],
When
P1 × V ≦ 700 × 10 ⁶ ,
P2 ≧ (0.0004 × (2α) ^3.6 ) × cos (θ + 2α) / (π × sin (2α) × b2 × L), and
2α> 4
One-way clutch characterized by being.
However,
F1: Load on the contact surface during rotation Fs × cos (θ + 2α) / sin (2α) −m × (R1 + R2) × ω ² [N]
F2: Load on the contact surface at rest Fs × cos (θ + 2α) / sin (2α) [N]
π: Pi ratio
L: Effective length of the contact surface of the roller (roller length-2 x chamfered portion) [m]
b1: Contact width of the contact surface of the roller during rotation (8 × F1 × R / (π × E × L)) ^1/2 [m]
b2: Contact width of the contact surface of the roller at rest (8 × F2 × R / (π × E × L)) ^1/2 [m]
Fs: Spring force at the set position [N]
m: Mass of the roller [kg]
θ: Angle in the direction in which the elastic body pushes [°]
ω: angular velocity of the outer ring ω = (Fs × cos (θ + 2α) / sin (2α) / (2 × m × (R1 + R2))) ^1/2 [rad / s]
R: Equivalent curvature of the roller and the inner ring R = 1 / (1 / R1 + 1 / R2) [m]
R1: Curvature radius of the cylindrical surface [m]
R2: Curvature radius of the roller [m]
E: Equivalent Young's modulus of the roller and the inner ring E = 2 / ((1−ν1 ² ) / E1 + (1−ν2 ² ) / E2) [Pa]
E1: Young's modulus of the inner ring [Pa]
E2: Young's modulus of the roller [Pa]
ν1: Poisson's ratio of the inner ring ν2: Poisson's ratio of the roller. A pulley device with a built-in clutch that is attached to a rotating shaft of an automobile auxiliary machine and is used by being laid over a belt that transmits power to and from a crank pulley,
A one-way clutch according to claim 1, wherein the pulley device has a built-in clutch.

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