JP2006132619A - Rotation transmission device with built-in one-way clutch - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotation transmission device with a built-in one-way clutch capable of surely performing locking operation of the one-way clutch in a wide temperature range from a low temperature to a high temperature, and capable of achieving long life of a support bearing. <P>SOLUTION: This rotation transmission device is provided with a sleeve 1 as an inside member; a pulley 2 as an outside member concentrically arranged around the sleeve 1; a roller clutch 3 as the one-way clutch arranged between an outer peripheral surface of the sleeve 1 and an inner peripheral surface of the pulley 2, and capable of transmitting rotation force between the pulley 2 and the sleeve 1 only when the pulley 2 tends to be relatively rotated in a predetermined direction with respect to the sleeve 1; and the support bearing 4 arranged between the outer peripheral surface of the sleeve 1 and the inner peripheral surface of the pulley 2 and supporting the pulley 2 so as to be relatively rotatable with respect to the sleeve 1 while supporting a radial load applied to the pulley 2. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a rotation transmission device with a built-in one-way clutch that is suitably used for a pulley device for driving an automotive auxiliary machine such as an alternator.

  2. Description of the Related Art Conventionally, a pulley device with a built-in one-way clutch for driving an alternator that generates electric power necessary for an automobile using an automobile traveling engine as a drive source is known (see, for example, Patent Document 1).

  As shown in FIG. 1 and FIG. 2, a one-way clutch built-in pulley device disclosed in Patent Document 1 includes a sleeve (inner member) 1 and a pulley (outer member) arranged concentrically outside the sleeve 1. ) 2 and between the outer peripheral surface of the sleeve 1 and the inner peripheral surface of the pulley 2, and only when the pulley 2 tends to rotate relative to the sleeve 1 in a predetermined direction, A roller clutch (one-way clutch) 3 that transmits a rotational force between the pulley 2 and the sleeve 1 is provided at both axial positions of the roller clutch 3 to support a radial load acting on the pulley 2. However, a support bearing 4 is provided that allows relative rotation between the sleeve 1 and the pulley 2.

  The sleeve 1 is externally fitted and fixed to a rotating shaft of an auxiliary machine such as an alternator, and can rotate together with the rotating shaft. The outer periphery of the pulley 2 has a corrugated cross section, and an endless belt is stretched between the pulley 2 and a driving pulley fixed to an end of an engine crankshaft or the like. Then, engine power is transmitted to the pulley 2 via the crankshaft, the drive pulley, and the endless belt.

  The roller clutch 3 includes a clutch inner ring 5 fitted to the sleeve 1, a clutch outer ring 6 fitted to the pulley 2, and a clutch retainer between the outer peripheral surface of the clutch inner ring 5 and the inner peripheral surface of the clutch outer ring 6. 8, a plurality of rollers 7 disposed via 8, and a spring 3 a that is disposed between the clutch holder 8 and the rollers 7 and presses the plurality of rollers 7 in one circumferential direction.

  The outer peripheral surface of the clutch inner ring 5 is provided with ramp portions 10 recessed in the radial direction at equal intervals in the circumferential direction, and the roller 7 can be rolled by the clutch holder 8 in the ramp portion 10. And is supported so as to be slightly displaceable in the circumferential direction. The ramp portion 10 has a cam surface 9 that is formed so as to be inclined so that the radial width dimension gradually decreases with respect to the inner peripheral surface of the clutch outer ring 6 as it goes in one circumferential direction. .

  The clutch retainer 8 is a molded product made of synthetic resin or the like, and its inner peripheral edge is engaged with a part of the cam surface 9 to prevent relative rotation with respect to the clutch inner ring 5, and the inner periphery of the end. The convex portion 11 formed on the surface is sandwiched between the axial end surface of the clutch inner ring 5 and the step surface 12 provided on the outer peripheral surface of the sleeve 1, thereby positioning in the axial direction.

  The support bearing 4 includes a plurality of bearings between the raceway surface 13 of the bearing outer ring 14 fitted to the inner peripheral surface of the end of the pulley 2 and the raceway surface 15 of the bearing inner ring 16 fitted to the outer peripheral surface of the end of the sleeve 1. The rolling elements 17 are disposed so as to be able to roll in the circumferential direction via the cage 20, and sealing devices 18 are mounted on the inner circumferential portions of both ends in the axial direction of the outer ring 14.

  In the pulley device with a built-in one-way clutch assembled in such a state, the roller 7 of the roller clutch 3 is engaged with the cam surface 9 of the clutch inner ring 5 when the traveling speed of the endless belt is constant or tends to increase. If the rotational force is transmitted from the pulley 2 to the rotating shaft via the roller clutch 3 and the sleeve 1 and the traveling speed of the endless belt tends to decrease, the roller 7 of the roller clutch 3 The clutch inner ring 5 is disengaged from the cam surface 9 to freely rotate the pulley 2 and the rotation shaft.

As a result, even when the rotational angular speed of the crankshaft of the engine fluctuates, the endless belt and the pulley 2 are prevented from rubbing, preventing the endless belt from being shortened due to the generation of abnormal noise and wear, and the power generation efficiency of the alternator Is prevented from falling.
JP 2002-130433 A

  The roller clutch 3 and the support bearing 4 are generally grease-lubricated. In the above-described pulley apparatus with a built-in one-way clutch, the roller clutch 3 and the support bearing 4 are partitioned using a sealing device 18, and the inside of the roller clutch 3 is separated. The space is filled with a first grease suitable for sliding contact lubrication, and the support bearing 4 is filled with a second grease suitable for rolling contact. Thereby, according to the contact state of the roller clutch 3 and the support bearing 4, sufficient durability is imparted to the first and second greases, respectively, and the durability of the roller clutch 3 and the support bearing 4 is ensured. Yes.

  However, it is necessary to replenish the roller clutch 3 and the support bearing 4 with greases having different components, which may increase the cost required for maintenance of the pulley device with a built-in one-way clutch. Therefore, it is desirable to lubricate the roller clutch 3 and the support bearing 4 using a common grease.

  Here, in order to engage the roller 7 of the roller clutch 3 with the cam surface 9 of the clutch inner ring 5 so as to transmit the rotational force between the sleeve 1 and the pulley 2, the elasticity of the spring 3a is required. Each roller 7 is pressed in the circumferential direction by force, and the radial width between the cam surface 9 of the clutch inner ring 5 that rotates with the sleeve 1 and the inner peripheral surface of the clutch outer ring 6 that rotates with the pulley 2. It is necessary to apply the wedge effect by pressing against the portion where the size is reduced.

  At this time, when a grease film exists on the cam surface 9 and the inner peripheral surface of the clutch outer ring 6, each roller 7 is pressed against the cam surface 9 while pushing the grease film. In order to realize the operation, it is preferable that the force required to press each roller 7 is substantially constant regardless of whether or not a grease film is present. For this purpose, it is important that the grease does not inhibit the pressing of the roller 7 even at a low temperature when the viscosity of the grease increases (the fluidity decreases).

  Further, in order to extend the life of the support bearing 4, it is important that the grease has excellent lubricity and durability under conditions such as high temperature and high speed rotation.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to ensure the locking operation of the one-way clutch over a wide temperature range from a low temperature to a high temperature and to provide a long service life for the support bearing. An object of the present invention is to provide a rotation transmission device with a built-in one-way clutch capable of achieving

In order to achieve the above-described object, a rotation transmission device with a built-in one-way clutch according to the present invention includes an inner member, an outer member disposed concentrically around the inner member, an outer peripheral surface of the inner member, and the Rotational force between the outer member and the inner member only when the outer member is disposed between the inner peripheral surface of the outer member and tends to rotate relative to the inner member in a predetermined direction. A one-way clutch capable of transmitting the inner member, and an outer member disposed between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member, while supporting a radial load applied to the outer member, A support bearing for supporting relative rotation with respect to the member,
The one-way clutch and the support bearing are lubricated with a common grease, the kinematic viscosity at 100 ° C. of the base oil contained in the grease is 5 to 15 mm ² / s, and the consistency of the grease at 0 ° C. The apparent viscosity at 150 to 300 and a shear rate of 200 s- ¹ at 0 ° C. is 10 to 90 Pa · s.

According to the present invention, the one-way clutch and the support bearing are lubricated with a common grease, and the kinematic viscosity at 100 ° C. of the base oil contained in the grease is 5 to 15 mm ² / s. Since the consistency at 150 is 300 to 300 and the apparent viscosity is 10 to 90 Pa · s at a shear rate of 200 s ⁻¹ at 0 ° C., the locking operation of the one-way clutch is ensured over a wide temperature range from low temperature to high temperature. And a long life of the support bearing can be achieved.

  The present invention has been briefly described above. Furthermore, the details of the present invention will be further clarified by reading through the best mode for carrying out the invention described below with reference to the accompanying drawings.

  Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings. In this embodiment, as the one-way clutch built-in type rotation transmission device, the one having the same structure as the one-way clutch built-in type pulley device already shown in FIGS. 1 and 2 is adopted. This will be described with reference to FIG.

In the pulley device with a built-in one-way clutch according to an embodiment of the present invention, the roller clutch 3 and the support bearing 4 are lubricated with a common grease G with reference to FIG. 1 and FIG. The kinematic viscosity at 100 ° C. of the base oil is 5 to 15 mm ² / s, the consistency of grease G at 150 ° C. is 150 to 300, and the apparent viscosity at 0 ° C. and a shear rate of 200 s ⁻¹ is 10 to 90 Pa · s. It is said that.

  As the base oil of the grease G composition, a mineral lubricating oil or a synthetic lubricating oil can be used. Although it does not restrict | limit especially as mineral-type lubricating oil, Paraffin-type mineral oil, naphthenic mineral oil, those mixed lubricating oils, etc. can be illustrated. Further, the synthetic lubricating oil is not particularly limited, and examples thereof include synthetic hydrocarbon oil, ether oil, ester oil, fluorine oil, and the like.

  Specifically, poly-α-olefin oil or the like can be used as the synthetic hydrocarbon oil. As the ether oil, dialkyl diphenyl ether oil, alkyl triphenyl ether oil, alkyl tetraphenyl ether oil, and the like can be used. As the ester oil, diester oil, neopentyl type polyol ester oil, complex ester oil, aromatic ester oil, and the like can be used. As the fluorine oil, perfluoroether oil, fluorosilicone oil, chlorotrifluoroethylene oil, fluorophosphazene oil, and the like can be used.

  The above base oils may be used alone or in appropriate combination. Among these, in consideration of lubricity and durability under conditions such as high temperature and high speed rotation, it is preferable that a synthetic lubricating oil is included, and particularly that an ester oil is included.

  In addition, ester oil has a characteristic that it is more polar than other lubricating oils described above and has excellent impact resistance during sliding friction, and diester oil, polyol ester oil, aromatic ester oil, etc. are preferably used. be able to.

Specifically, dioctyl adipate (DOA), diisobutyl adipate (DIBA), dibutyl adipate (DBA), dioctyl azelate (DOZ), dibutyl sebacate (DBS), dioctyl sebacate (DOS), etc. are used as the diesel oil. It can be illustrated. Examples of polyol ester oils include pentaerythritol ester oils, dipentaerythritol ester oils, tripentaerythritol oils, neopentyl diol ester oils, trimethylolpropane ester oils and the like in which C _{4 to} C ₁₈ alkyl chains are derived. It can be illustrated. Examples of the aromatic ester oil include polyol ester oil, trioctyl trimellitate (TOTM), tridecyl trimellitate, tetraoctyl pyromellitate and the like. These may be used alone or in appropriate combination.

The kinematic viscosity of the base oil is 5 to 15 mm ² / s, preferably 5 to 10 mm ² / s at 100 ° C. When the kinematic viscosity at 100 ° C. is less than 5 mm ² / s, for example, between the raceway surface 13 of the bearing outer ring 14 and the rolling surface of the rolling element 17 or between the raceway surface 15 of the bearing inner ring 16 and the rolling element 17. There is a possibility that the oil film formed between the moving surface becomes too thin and the bearing durability is lowered. On the other hand, if it exceeds 15 mm ² / s, the engagement (locking performance) between the roller 7 of the roller clutch 3 and the cam surface 9 may be lowered.

  The grease G is blended with the above base oil, as a thickener, a substance that is colloidally dispersed in the base oil to make the base oil semi-solid or solid. Such thickeners include lithium soap, calcium soap, sodium soap, aluminum soap, lithium complex soap, calcium complex soap, sodium complex soap, barium complex soap, aluminum complex soap, etc. Metal soaps, inorganic compounds such as bentonite and clay, and organic compounds such as monourea, diurea, triurea, tetraurea, urethane and sodium terephthalate, etc. Of these, urea-based organic compounds can be preferably used. These thickeners may be used alone or in appropriate combination.

  The consistency of grease G at 0 ° C. is 150 to 300, more preferably 200 to 300. When the consistency at 0 ° C. is less than 150, the grease does not spread to the sliding contact portion (for example, the gap between the rolling surface of the roller 7 and the inner peripheral surface of the clutch outer ring 6) mainly when the roller clutch 3 slips. In addition, the elastic force of the spring 3a is also used for the locking operation of the roller clutch 3, but there is a possibility that the movement of the spring 3a may be hindered. On the other hand, if the consistency exceeds 300, there is a risk that grease may easily flow out due to vibration during traveling.

Furthermore, the apparent viscosity of the grease G at 0 ° C. and a shear rate of 200 s ⁻¹ is 10 to 90 Pa · s, more preferably 30 to 90 Pa · s. If the apparent viscosity at a shear rate of 200 s ⁻¹ at 0 ° C. is less than 10 Pa · s, there is a risk that the grease will easily flow out, and if greater than 90 Pa · s, the roller 7 of the roller clutch 3 There is a possibility that the engagement with the cam surface 9 is lowered.

  The blending amount of the thickener is not limited as long as grease can be formed with the base oil, but is 10 to 30% by weight, preferably 15 to 25% by weight of the total amount of grease.

  Furthermore, in order to further improve the performance of the grease G, various additives such as an extreme pressure agent, an antioxidant, a rust inhibitor, an oil agent, and a metal deactivator may be mixed as desired.

  As the extreme pressure agent, an extreme pressure agent such as phosphorus-based, zinc dithiophosphate, and organic molybdenum can be used. And organic molybdenum compounds such as molybdenum dialkyldithiophosphate, molybdenum diaryldithiophosphate, molybdenum dialkyldithiocarbamate, thiocarbamine compounds, phosphates, phosphites, and the like.

  As the antioxidant, generally used antioxidants can be used. For example, amine-based such as phenyl-1-naphthylamine, phenol-based such as 2,6-di-tert-dibutylphenol, sulfur-based An antioxidant such as zinc dithiophosphate can be exemplified.

  Antirust agents include organic sulfonates such as alkali metals and alkaline earth metals, alkyls such as alkyls and alkenyl succinic acid esters, alkenyl succinic acid derivatives, partial esters of polyhydric alcohols such as sorbitan monooleate, etc. A rust preventive agent can be illustrated.

  Examples of the oily agent include oily improvers such as fatty acids and animal and vegetable oils.

  Examples of the metal deactivator include metal deactivators such as benzotriazole.

  In addition, said various additive may be used independently and may be used in combination as appropriate. Further, the addition amount is not particularly limited as long as it does not impair the object of the present invention.

  Moreover, in order to further improve the performance of the grease G, a known general additive conventionally used in grease can be contained as necessary.

  Grease G contains the above-described components, but there is no limitation on the production method. Moreover, after adding an additive, it is necessary to stir well and to disperse | distribute uniformly, but heating in that case is also effective.

  The grease G prepared as described above has fluidity even at low temperatures, and the roller 7 of the roller clutch 3 is connected to the clutch inner ring 5 so as to transmit the rotational force between the sleeve 1 and the pulley 2. When the cam surface 9 is engaged and locked, the force required to press each roller 7 against the cam surface 9 is substantially constant. Thereby, the clutch operation of the roller clutch 3 can be performed reliably.

  Furthermore, the grease G is excellent in lubricity and durability under conditions of high temperature and high speed rotation, can be suitably used for lubrication of the support bearing 4, and can extend the life of the support bearing 4. The roller clutch 3 and the support bearing 4 can be lubricated with the common grease G, and the maintenance cost of the one-way clutch built-in rotation transmission device can be reduced.

  In the above-described embodiment, since the roller clutch 3 and the support bearing 4 are lubricated by the common grease G, the sealing device 18 provided at the end of the support bearing 4 on the roller clutch 3 side is necessarily required. is not.

(Second Embodiment)
Next, with reference to FIG. 3, the one-way clutch built-in type pulley apparatus which is 2nd Embodiment of the one-way clutch built-in type rotation transmission apparatus which concerns on this invention is demonstrated. FIG. 3 is a cross-sectional view illustrating a pulley device with a built-in one-way clutch according to a second embodiment. In addition, the same code | symbol is attached | subjected about the member which is common in the one-way clutch built-in type pulley apparatus of 1st Embodiment mentioned above.

  The rotation transmission device with a built-in one-way clutch according to the present embodiment includes a sleeve (inner member) 101, a pulley (outer member) 102 disposed concentrically outside the sleeve 101, an outer peripheral surface of the sleeve 101, and a pulley 102. A roller clutch (one-way) that is provided between the inner peripheral surface and transmits rotational force between the pulley 102 and the sleeve 101 only when the pulley 102 tends to rotate relative to the sleeve 101 in a predetermined direction. Clutch) 103 and between the pulley 102 and the sleeve 101 are provided at both axial positions of the roller clutch 103, and the sleeve 101 and the pulley 102 can freely rotate relative to each other while supporting a radial load acting on the pulley 102. Support bearings 104 and 121 are provided.

  The sleeve 101 is externally fitted and fixed to a rotary shaft of an auxiliary machine such as an alternator, and can be rotated integrally with the rotary shaft. The outer periphery of the pulley 102 has a corrugated cross section, and an endless belt is stretched between the pulley 102 and a driving pulley fixed to an end of an engine crankshaft or the like. Engine power is transmitted to the pulley 102 via the crankshaft, the drive pulley, and the endless belt.

  The roller clutch 103 is disposed between a plurality of rollers 107 disposed between the outer peripheral surface of the sleeve 101 and the inner peripheral surface of the pulley 102 via a clutch retainer 108, and between the clutch retainer 108 and the roller 107. And a spring 103a that presses the plurality of rollers 107 in one circumferential direction.

  Ramp portions 110 that are recessed in the radial direction are provided on the outer peripheral surface of the sleeve 101 at equal intervals in the circumferential direction, and the roller 107 can be rolled by the clutch cage 108 in the ramp portion 110. Moreover, it is supported so as to be slightly displaceable in the circumferential direction. The ramp portion 110 has a cam surface 109 formed so as to be inclined so that the radial width dimension gradually decreases with respect to the inner peripheral surface of the pulley 102 as it goes in one direction in the circumferential direction.

  The clutch retainer 108 is formed of a synthetic resin or the like, and its inner peripheral edge is engaged with a part of the cam surface 109 to prevent relative rotation with respect to the sleeve 101, and the end side surface 111. Is engaged with a stepped portion 112 provided on the outer peripheral surface of the sleeve 101 to achieve axial positioning.

  In the support bearing 104, a plurality of balls 117 are arranged between a raceway surface 113 formed on the inner peripheral surface of the end of the pulley 102 and a raceway surface 115 formed on the outer peripheral surface of the end of the sleeve 101 via the cage 120. The outer peripheral edge portion of the sealing device 118 is fixed to the inner peripheral portion of the axial end portion of the pulley 102 on the outer side of the bearing, and the inner peripheral edge portion of the sealing device 118 is The seal groove 128 is slidably in contact with the outer peripheral surface.

  The support bearing 122 includes a raceway surface 124 formed on the inner peripheral surface of the end of the pulley 102 and a raceway surface 123 formed on the outer peripheral surface of the end of the sleeve 101 on the side opposite to the end where the support bearing 104 is provided. A plurality of rollers 122 are arranged so as to be able to roll in the circumferential direction via a cage 125, and the outer peripheral edge of the sealing device 126 is disposed on the inner peripheral part of the axial end of the pulley 102 on the outer side of the bearing. The inner peripheral edge of the sealing device 126 is in sliding contact with the outer peripheral surface of the sleeve 101.

  A sealing device 127 in which an outer peripheral edge portion is fixed to an inner peripheral portion of the axial end portion of the pulley 102 is provided further on the bearing outer side than the sealing device 126 of the support bearing 122. The inner peripheral edge of the sealing device 127 is in sliding contact with a seal groove 129 that is recessed in the outer peripheral surface of the sleeve 101.

  Both the roller clutch 103 and the support bearings 104 and 121 are lubricated with the grease G described above.

  EXAMPLES Next, although an Example and a comparative example are given and this invention is demonstrated further, this invention is not restrict | limited at all by this.

  First, for the greases of Examples 1 to 5 and Comparative Examples 1 to 3 prepared according to the compositions shown in Table 1 and Table 2, the low temperature characteristics (concentration, apparent viscosity) of each grease were measured, and each grease was enclosed. In addition, the locking performance of the one-way clutch was evaluated, and the seizure resistance of the support bearing filled with each grease was tested.

  The consistency of the grease was measured by a method according to JIS K2220, and the apparent viscosity was measured using a rheometer. FIG. 4 is a cross-sectional view showing a measurement unit of a rheometer that measures the rheological properties of grease.

As shown in FIG. 4, the measurement unit of the rheometer has a disk-shaped measurement plate 31 (parallel plate) placed above a flat plate stage 30 surrounded by a heat insulating wall (not shown). The flat lower surface of the measurement plate 31 is parallel to the stage 30. Then, the grease G is filled in the gap placed between the measurement plate 31 and the stage 30. While controlling the temperature of the grease G with a temperature control device built in the stage 30, the measuring plate 31 is rotated in one direction to apply a shear rate to the grease G, and the shear stress and the apparent viscosity are measured. The shear stress was measured at a temperature of −40 ° C. and a shear rate of 200 s ⁻¹ . The diameter of the measurement plate 31 was 20 mm, and the gap was 0.1 mm. Further, the measurement plate 31 may be a cone plate instead of the parallel plate. If the oscillation is given at an appropriate frequency, the viscoelasticity of the grease G can be measured. The lock performance was evaluated based on the followability of the rotation of the clutch inner ring with respect to the rotation of the clutch outer ring when locked in a low temperature atmosphere (0 ° C.). ○ in Tables 1 and 2 indicates the case where the rotation of the clutch inner ring stably follows the rotation of the clutch outer ring, and × indicates the case where the rotation of the clutch inner ring does not follow the rotation of the clutch outer ring. Show.

Next, in the seizure resistance test of the support bearing, as shown in FIG. 5, a plurality of rolling elements 17 can roll in the circumferential direction via the cage 20 between the bearing outer ring 14 and the bearing inner ring 16. A deep groove ball bearing with a sealing device (an inner diameter of 8 mm, an outer diameter of 22 mm, and a width of 7 mm) having a sealing device 18 mounted on each of the inner diameter portions of both ends in the axial direction of the outer ring 14 is used as a test bearing. The greases of Examples 1 to 5 and Comparative Examples 1 to 3 are filled so as to occupy 50% of the bearing space volume, and using a test machine similar to the ASTM D1741 bearing life tester, the test temperature is 150 ° C., the axial load is It was rotated at a rotational speed of 3000 min ⁻¹ under 59N conditions (other conditions conform to ASTM D1741), and the time until seizure occurred and the temperature of the outer ring 14 rose to 160 ° C. or higher was defined as the lifetime. Note that if the temperature did not rise to 160 ° C. or higher even after 3000 hours of rotation, the test was terminated. In the seizure resistance test, the time until the end of the above-mentioned life was measured for each grease four times, and the average value was used as the test result. In Tables 1 and 2, the results of Comparative Example 1 are shown. The test result is shown as a relative value with 1.0.

Tables 1 and 2 show the results. In Tables 1 and 2, the notes 1) to 11) are as follows.
1) Mineral oil: Kinematic viscosity at 100 ° C. 8.0 mm ² / s
2) Mineral oil: Kinematic viscosity at 100 ° C. 16.8 mm ² / s
3) Poly α-olefin oil: Kinematic viscosity at 100 ° C. 4.0 mm ² / s
4) Polyalphaolefin oil: kinematic viscosity at 100 ° C. 5.8 mm ² / s
5) Polyol ester oil: Kinematic viscosity at 40 ° C. 5.9 mm ² / s
6) Dialkyl diphenyl ether oil: Kinematic viscosity at 100 ° C. 12.6 mm ² / s
7) 12 hydroxystearic acid: azelaic acid = 75% by weight: 25% by weight of lithium composite soap 8) Diurea produced by reaction of 4'4-diphenylmethane diisocyanate and cyclohexylamine 9) Vanlube 81 (Vanderbit)
10) Naphtex zinc (manufactured by Nippon Chemical Industry)
11) Lubrizol 1195 (manufactured by Lubrizol)

From Table 1 and Table 2, the greases of Examples 1 to 5 are superior to the greases of Comparative Examples 1 to 3 in both the locking performance of the one-way clutch at low temperature and the seizure resistance of the support bearing. It can be seen that the one-way clutch can be reliably locked over a wide temperature range up to a high temperature (−40 ° C. to 160 ° C.) and a long life of the support bearing can be achieved. In particular, the kinematic viscosity at 100 ° C. of the base oil contained in the grease is 5 to 15 mm ² / s, the consistency of the grease at 200 ° C. is 200 to 300, and the apparent viscosity at 0 ° C. and a shear rate of 200 s ⁻¹ is 30. It can be seen that the greases of Examples 1 and 2 that fall within the range of ˜90 Pa · s have an extremely long bearing life. FIG. 6 shows the above results arranged in terms of the consistency and apparent viscosity at 0 ° C. of the grease. In FIG. 6, the hatched area is the range of the consistency and apparent viscosity of the grease defined in the present invention, and the greases of Examples 1 to 5 included in this area are out of this area. As compared with the greases of 3 to 3, it is excellent in both the locking performance of the one-way clutch and the seizure resistance of the support bearing as described above.

  In addition, this invention is not limited to each embodiment and Example mentioned above, In the range which does not deviate from the summary of this invention, it can change suitably.

  For example, in the first embodiment described above, the configuration in which the cam surface 9 is formed on the clutch inner ring 5 in the roller clutch 3 as a one-way clutch has been described, but the cam surface may be formed on the clutch outer ring 6. Similarly, in the above-described second embodiment, the configuration in which the cam surface 109 is formed on the outer peripheral surface of the sleeve 101 has been described, but the cam surface may be formed on the inner peripheral surface of the pulley 102. Further, the present invention can be applied to other types of one-way clutches such as lug clutches and cam clutches in place of the roller clutches 3 and 103.

  In the first embodiment described above, the case where the pair of support bearings 4 and 4 are provided on both sides of the roller clutch 3 in the axial direction is illustrated. However, the support bearing 4 is provided only on one side of the roller clutch 3 in the axial direction. You may do it. Furthermore, in the embodiment described above, the pulley 2 is exemplified as the outer member, but a gear can be used as the outer diameter member.

  In the second embodiment described above, the sealing devices 118, 126, and 127 have been described as a configuration in which the outer peripheral edge portion is fixed to the pulley 102 and the inner peripheral edge portion is in sliding contact with the sleeve 101. It is good also as a structure which is fixed to the sleeve 101 and an outer peripheral edge part is slidably contacted with the pulley 102.

  Further, in each of the above-described embodiments, the pulley device with a built-in one-way clutch that is mounted on the rotating shaft of an auxiliary machine such as an alternator has been exemplified. The present invention may be applied to a pulley device with a built-in one-way clutch that is mounted on a rotating shaft or the like of a machine drive device. When used as an auxiliary machine drive device during engine idle stop, this pulley device is mounted on the end of the engine crankshaft or the drive shaft of the electric motor. As a result, when one device of the engine and the electric motor is in the operating state and the other device is in the stopped state, the rotation force is transmitted from the rotating shaft of the one device in the operating state to the pulley 2. While making it free, the rotation shaft of the other device is prevented from rotating.

  In addition, the materials, shapes, dimensions, forms, numbers, placement locations, etc. of the rotary shaft, inner diameter side member, outer diameter side member, one-way clutch, support bearing, etc. exemplified in the above embodiment can achieve the present invention. It is optional and not limited.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view showing a pulley device with a built-in one-way clutch that is a first embodiment of a rotation transmission device with a built-in one-way clutch according to the present invention. It is II-II arrow sectional drawing of FIG. It is sectional drawing which shows the pulley apparatus with a one-way clutch which is 2nd Embodiment of the rotation transmission apparatus with a built-in one-way clutch which concerns on this invention. It is a schematic sectional drawing which shows the measurement part of the rheometer which measures the rheological characteristic of grease. It is sectional drawing of a test bearing. It is a graph which shows the consistency and apparent viscosity range of the grease prescribed | regulated by this invention.

Explanation of symbols

1 Sleeve (inner member)
2 Pulley (outer member)
3 Roller clutch (one-way clutch)
4 Support bearing G Grease

Claims (1)

An inner member;
An outer member disposed concentrically around the inner member;
The outer member and the inner member are disposed between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member, and only when the outer member tends to rotate relative to the inner member in a predetermined direction. A one-way clutch capable of transmitting rotational force to and from the member;
A support disposed between the outer peripheral surface of the inner member and the inner peripheral surface of the outer member, and supports the outer member so as to be relatively rotatable with respect to the inner member while supporting a radial load applied to the outer member. A bearing,
With
The one-way clutch and the support bearing are lubricated by a common grease;
The kinematic viscosity at 100 ° C. of the base oil contained in the grease is 5 to 15 mm ² / s,
One-way clutch built-in rotation transmission device, wherein the grease has a consistency of 150 to 300 at 0 ° C. and an apparent viscosity of 10 to 90 Pa · s at a shear rate of 200 s ⁻¹ at 0 ° C.

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