JP2010266017A - 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, having improved wear resistance and seizure resistance under high-temperature and high-speed conditions. <P>SOLUTION: A pulley device 1 with a built-in roller clutch includes a sleeve 2, a pulley 3, a rolling bearing 4, and the roller clutch 5. The roller clutch 5 as the one-way clutch includes a clutch inner ring 6, a clutch outer ring 9, and a roller 10 arranged between the outer peripheral face of the clutch inner ring 6 and the inner peripheral face of the clutch outer ring 9. With the connection of the pulley 3 to the sleeve 2, it transmits rotating force only to rotate the pulley 3 relative to the sleeve 2 in a predetermined direction, from the pulley 3 to the sleeve 2. The clutch inner ring 6 is formed of a steel material having higher hardness Hv at 100°C than a raw material for each of the clutch outer ring 9 and the roller 10, the hardness Hv being 700 or greater at 100°C. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a rotation transmission device with a built-in one-way clutch.

Conventionally, rotation transmission with built-in one-way clutch is used as a pulley device mounted on a rotating shaft of an auxiliary machine for an automobile such as an alternator, a rotating shaft of an auxiliary driving device, or a crank shaft of an engine mounted on an idling stop vehicle. The device is known.
For example, a one-way clutch built-in type rotation transmission device incorporated in an alternator includes a driven pulley over which a driving belt is stretched from a driving pulley fixed to an engine crankshaft, and a sleeve fixed to the rotating shaft of the alternator. A one-way clutch and a pair of support bearings are provided between the driven pulley and the sleeve.

  When the rotational angular speed of the driven pulley is faster than the rotational angular speed of the rotating shaft of the alternator, the driven pulley and the sleeve cannot rotate relative to each other due to the wedge effect of the roller of the one-way clutch (the locked state). It is transmitted to the rotating shaft. On the other hand, when the rotational angular velocity of the driven pulley is slower than the rotational angular velocity of the rotating shaft of the alternator, the driven pulley and the sleeve can rotate freely (overrun state). Therefore, even when the rotational angular velocity of the crankshaft fluctuates, the drive belt and the pulley are prevented from rubbing due to the action of the one-way clutch, and the generation of abnormal noise called squeal and the life reduction of the drive belt due to friction are prevented. At the same time, the power generation efficiency of the alternator is prevented from decreasing.

  Such a rotation transmission device with a built-in one-way clutch is generally lubricated with grease. For example, a rotation transmission device with a built-in one-way clutch disclosed in Patent Document 1 includes an inner member fixed to a rotating shaft, a cylindrical outer member arranged concentrically with the inner member, and an outer peripheral surface and an outer surface of the inner member. A one-way clutch provided between the inner peripheral surface of the member and a support bearing provided adjacent to the one-way clutch and rotatably supporting the inner member and the outer member.

Grease suitable for sliding contact lubrication is sealed in the internal space of the one-way clutch, and another type of grease suitable for rolling contact is sealed in the internal space of the support bearing. And the following performance is calculated | required by the grease which lubricates a one-way clutch.
(1) Low friction and low wear characteristics during sliding (2) Stability over a wide temperature range (eg, -40 ° C to 160 ° C) (3) Abrasion resistance and fire resistance when used under high temperature and high speed conditions In other words, the one-way clutch incorporated in the one-way clutch built-in rotation transmission device disclosed in Patent Document 1 has a plurality of rollers arranged between the outer peripheral surface of the clutch inner ring and the inner peripheral surface of the clutch outer ring. The inner ring of the clutch and the outer ring of the clutch are connected when the roller bites and engages between the two peripheral surfaces. The outer peripheral surface of the clutch inner ring and the inner peripheral surface of the clutch outer ring and the rolling surface of the roller There may be a slip between the two. In order to reduce the deterioration of grease due to heat generation due to friction at the sliding contact part and wear of the sliding contact part, and to stabilize the long-term operation of the one-way clutch, the grease that lubricates the sliding contact part is low. Friction and low wear are important.

  Further, in order to lock the one-way clutch so as to transmit the rotational force between the inner member and the outer member of the one-way clutch built-in rotation transmission device, the one-way clutch roller is used by an elastic force such as a spring. To the outer peripheral surface of the clutch inner ring and the inner peripheral surface of the clutch outer ring. At this time, there is a grease film between the outer peripheral surface of the clutch inner ring of the one-way clutch and the inner peripheral surface of the clutch outer ring and the rolling surface of each roller, and each roller pushes the grease film while pushing the outer periphery of the clutch inner ring. It is pressed against the inner peripheral surface of the surface and the outer ring of the clutch.

  In order for a one-way clutch to perform a stable clutch operation, it is preferable that the force required to press the roller is almost constant regardless of the presence or absence of the grease film. It is important that the grease does not impede the pressing of the roller against the outer peripheral surface of the inner ring of the clutch and the inner peripheral surface of the outer ring of the one-way clutch even at a low temperature where fluidity is reduced.

  Furthermore, the rotation transmission device with a built-in one-way clutch is required to have reliable engagement and durability of the rollers. In addition, the temperature in the engine room has increased with the recent sealing of the automobile engine room. Since the temperature is high, wear resistance and seizure resistance at high temperatures are also required. Furthermore, the one-way clutch built-in type rotation transmission device for an alternator tends to become a high rotation speed as the automobile is electrically equipped. Therefore, the wear resistance and seizure resistance of the one-way clutch under high speed conditions are required.

JP 2002-130433 A JP 2005-207575 A JP 2005-234638 A JP 2008-106147 A JP 2008-127491 A

  However, the grease that lubricates the one-way clutch described in Patent Document 1 has improved durability against sliding contact (fretting resistance and heat resistance), and reduces heat generation due to friction at the sliding contact portion. It wasn't something to do. This heat generation causes the temperature of the rotation transmission device with a built-in one-way clutch to rise, and for example, the stable clutch operation is hindered by the difference in the coefficient of thermal expansion between the inner ring and outer ring of the one-way clutch and the roller. There was a risk of this.

In addition, there is a limit to the wear resistance and seizure resistance under high-temperature and high-speed conditions in terms of grease lubrication and wear suppression with wear inhibitors added to grease.
SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to solve the above-described problems of the prior art and to provide a one-way clutch built-in rotation transmission device that is excellent in wear resistance and seizure resistance under high temperature and high speed conditions. To do.

  In order to solve the above problems, the present invention has the following configuration. That is, the one-way clutch built-in type rotation transmission device according to the present invention includes an inner rotation member, an outer rotation member concentrically arranged around the inner rotation member, and the both rotation members arranged between the rotation members. A rolling bearing that supports the member so as to be relatively rotatable, and the rotating member that is disposed between the rotating members and that rotates only one of the rotating members relative to the other in a predetermined direction is connected to the rotating members. A one-way clutch built-in type rotation transmission device comprising: an inner clutch member fixed to an outer peripheral surface of the inner rotating member; and an inner clutch member around the inner clutch member. An outer clutch member concentrically disposed and fixed to an inner peripheral surface of the outer rotating member, and a plurality of engagement elements disposed between the outer peripheral surface of the inner clutch member and the inner peripheral surface of the outer clutch member The clutch is connected to the outer peripheral surface of the inner clutch member and the inner peripheral surface of the outer clutch member to connect the both clutch members and transmit the rotational force. And the inner clutch member is made of a steel material having a hardness Hv at 100 ° C. higher than that of the material constituting the outer clutch member and the engagement element and a hardness Hv at 100 ° C. of 700 or more. It is characterized by.

  In the one-way clutch built-in type rotation transmission device according to the present invention, at least one of the inner clutch member, the outer clutch member, and the engagement element comprises 0.2% by mass or more and less than 0.6% by mass of carbon. Contains 0.5% to 2% by mass of silicon, 0.5% to 1% by mass of manganese, 1% to 2% by mass of chromium, and 0.5% to 2% by mass of molybdenum. It is preferable that the hardness Hv at 100 ° C. is 700 or more after being carbonitrided.

  In addition, at least the inner clutch member among the inner clutch member, the outer clutch member, and the engagement element is 0.2% by mass or more and less than 0.6% by mass of carbon, and 0.5% by mass or more and 2% by mass of silicon. %, Less than 1% by mass of manganese, less than 1% by mass to less than 2% by mass of chromium, more than 0.5% by mass and less than 2% by mass of molybdenum, and It is preferable that carbonitriding is performed and the hardness Hv at 100 ° C. is 700 or more.

  Furthermore, lubrication between the inner clutch member and the outer clutch member and the engagement element may be performed with grease.

  The one-way clutch built-in type rotation transmission device of the present invention is excellent in wear resistance and seizure resistance under high temperature and high speed conditions.

It is a longitudinal cross-sectional view which shows the structure of the pulley apparatus with a built-in roller clutch which is one Embodiment of the rotation transmission apparatus with a built-in one-way clutch which concerns on this invention. It is AA sectional drawing of FIG. 1 which expanded and showed only the one way clutch. It is the elements on larger scale which expanded and showed the spring in a one-way clutch, and its peripheral part.

  An embodiment of a rotation transmission device with a built-in one-way clutch according to the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view showing the structure of a roller clutch built-in pulley device which is an embodiment of a one-way clutch built-in rotation transmission device according to the present invention. 2 is an AA cross-sectional view of FIG. 1 showing only the roller clutch in an enlarged manner. FIG. 3 is a partially enlarged view showing the spring in the roller clutch and its peripheral portion in an enlarged manner (viewed from the radial direction).

  A pulley apparatus 1 with a built-in roller clutch shown in FIG. 1 includes a substantially cylindrical sleeve 2 (inner rotating member) that can be externally fixed to a rotating shaft (not shown), and a substantially cylinder that is arranged around the sleeve 2 and concentrically with the sleeve 2. And a pulley 3 (outer rotating member) having a shape. A pair of rolling bearings 4 and 4 (a deep groove ball bearing is shown in FIG. 1) are arranged at both ends in the axial direction between the outer peripheral surface of the sleeve 2 and the inner peripheral surface of the pulley 3. A roller clutch 5 is arranged at the center in the direction.

The rolling bearings 4 and 4 support the sleeve 2 and the pulley 3 so as to be relatively rotatable while supporting a radial load applied to the pulley 3. The roller clutch 5 is a one-way clutch that transmits only the rotational force that rotates the pulley 3 relative to the sleeve 2 in a predetermined direction by connecting the pulley 3 and the sleeve 2 to the sleeve 2. is there.
Here, the roller clutch 5 will be described in more detail with reference to FIGS. The roller clutch 5 includes a clutch inner ring 6 (inner clutch member) that is externally fitted and fixed to the outer peripheral surface of the sleeve 2, and is arranged around the clutch inner ring 6 concentrically with the clutch inner ring 6, and on the inner peripheral surface of the pulley 3. The clutch outer ring 9 (outer clutch member) fitted and fixed, a plurality of rollers 10 (engagement elements) disposed between the outer peripheral surface of the clutch inner ring 6 and the inner peripheral surface of the clutch outer ring 9, and the outer periphery of the clutch inner ring 6 A cage 11 that holds the roller 10 is provided between the surface and the inner peripheral surface of the clutch outer ring 9.

  On the outer peripheral surface of the clutch inner ring 6, a plurality of concave portions 7 called ramp portions are formed side by side in the circumferential direction at equal intervals, and the outer peripheral surface is a cam surface 8. Further, the inner peripheral surface of the clutch outer ring 9 is a cylindrical surface 17 except for both ends in the axial direction. The depth of the concave portion 7 is not constant and gradually decreases along the circumferential direction (in FIG. 2, it gradually decreases toward the right side). As a result, a wedge-shaped gap between the outer peripheral surface of the clutch inner ring 6 and the inner peripheral surface of the clutch outer ring 9 gradually decreases in the radial direction toward one circumferential direction (rightward in FIG. 2). A plurality of spaces are formed.

  In the most part (deep part) where the recess 7 is formed (ramp part), the distance between the outer peripheral surface of the clutch inner ring 6 and the inner peripheral surface of the clutch outer ring 9 is larger than the diameter of the roller 10, The diameter gradually decreases along the direction to be the same as the diameter of the roller 10, and is slightly smaller than the diameter of the roller 10 at the shallowest portion. In the portion where the recess 7 is not formed (cylindrical surface portion), the distance between the outer peripheral surface of the clutch inner ring 6 and the inner peripheral surface of the clutch outer ring 9 is smaller than the diameter of the roller 10. Further, flanges 16a and 16b having inward flange shapes are formed at both axial ends of the clutch outer ring 9.

  The cage 11 holds the roller 10 so that it can roll and slightly displace in the circumferential direction. A spring 13 that elastically presses the roller 10 is disposed between the column portion 12 of the cage 11 and the roller 10, and the roller 10 causes the roller 10 to face the cylindrical surface portion from the ramp portion (see FIG. 2 is pressed to the right). Therefore, the roller 10 bites into engagement between the outer peripheral surface of the clutch inner ring 6 and the inner peripheral surface of the clutch outer ring 9 (engagement) in the vicinity of the boundary portion between the ramp portion and the cylindrical surface portion (the shallow portion of the recess 7). Will be).

  Therefore, when the clutch outer ring 9 rotates relative to the clutch inner ring 6 and the relative rotation direction is the same as the pressing direction of the roller 10, the clutch inner ring 6 and the clutch outer ring 9 are Are connected and rotate together (locked state). On the other hand, when the relative rotation direction of the clutch outer ring 9 is opposite to the pressing direction of the roller 10, the roller 10 rolls in a deep portion of the ramp portion. No torque is transmitted between the clutch and the outer ring 9 (overrun state).

Here, an example of the cage 11 and the spring 13 will be described in more detail with reference to FIGS.
A plurality of rollers 10, a cage 11, and a spring 13 are arranged in a cylindrical gap between the cam surface 8 of the clutch inner ring 6 and the cylindrical surface 17 of the clutch outer ring 9. The spring 13 is, for example, a leaf spring obtained by bending a steel plate into a substantially triangular shape, and is composed of austenitic stainless steel or precipitation hardening stainless steel, and is subjected to an aging treatment so that the hardness is Hv 500 or more and less than 600. Yes.

  The cage 11 is formed by integrally forming a resin composition such as polyamide 46 containing glass fibers in a cage-type cylindrical shape, and a pair of rim portions 18 and 18 having an annular shape. The rim portions 18 and 18 are provided with a column portion 12 that connects the rim portions 18 and 18. The roller 10 is rotatably held in a pocket which is a portion surrounded by four sides by the inner side surfaces of the rim portions 18 and 18 and the side surfaces of the column portions 12.

  Further, a convex portion 19 is formed on the inner diameter surface of the rim portion 18 on one side (left end side in FIG. 1) so as to protrude inward in the radial direction. By holding the convex portion 19 between the sleeve flange portion 20 formed in the portion of the outer peripheral surface of the sleeve 2 facing the flange portion 16a and the axial end surface of the clutch inner ring 6, the cage 11 is pivoted. It is prevented that the retainer 11 is displaced in the direction, and the cage 11 is prevented from rotating relative to the clutch inner ring 6 (sleeve 2).

  Further, both end side support plate portions 21 and 21 protrude radially outward from the outer peripheral side surface of the column part 12 at the inner side surfaces of the rim units 18 and 18 that are aligned with the circumferential intermediate portion of the column unit 12. It is formed in a state. Furthermore, the center side support plate part 22 is formed in the center part of the column part 12 in the state which protrudes in a radial direction outward from the outer peripheral side surface of the column part 12. FIG. The both end side support plate portions 21 and 21 and the center side support plate portion 22 are provided in a state slightly shifted in the circumferential direction, and one end surface in the circumferential direction of the both end side support plate portions 21 and 21 (FIG. 2). -3) and the other side surface in the circumferential direction of the central support plate 22 (left side surface in FIGS. 2-3), the base 23 of the spring 13 is sandwiched. In this state, a locking protrusion 26 formed at the tip of the central support plate 22 is engaged with the outer peripheral edge of the central portion of the base 23. Therefore, regardless of the centrifugal force applied during operation, the spring 13 does not fall out of the cage 11 in the radial direction.

  The spring 13 is formed by bending both end portions of the base portion 23 at an acute angle in the same direction in the circumferential direction and providing pressing portions 24, 24 at both end portions. As described above, the spring 13 has both side surfaces of the base 23 on one side in the circumferential direction of the support plates 21 and 21 at both ends, and the center of the base 23 on the other side in the circumferential direction of the center support plate 22. The other side surfaces are elastically contacted with each other to be locked at a plurality of locations in the circumferential direction of the cage 11. And the roller 10 is elastically pressed toward the shallow side (right side of FIG. 2) of the recessed part 7 by the press parts 24 and 24. FIG.

  In this roller clutch built-in type pulley apparatus 1, the spring 13 having the above-described configuration is used, so that even if the overrun state and the locked state are repeated, the spring 13 is unlikely to be worn or sag. For this reason, the grease is deteriorated by the abrasion powder of the spring 13, and the contact portion between the roller 10 and the outer peripheral surface of the clutch inner ring 6 or the inner peripheral surface of the clutch outer ring 9 is seized, or the spring 13 is in a locked state. It is possible to prevent the idling phenomenon from occurring at the time of power. Therefore, the durability of the roller clutch 5 is improved, and the durability and reliability of the roller clutch built-in pulley device 1 incorporating the roller clutch 5 is improved.

  Further, in this roller clutch built-in type pulley apparatus 1, the roller clutch 5 and the rolling bearing 4 are lubricated by a grease composition (not shown). That is, lubrication between the outer peripheral surface of the clutch inner ring 6 and the inner peripheral surface of the clutch outer ring 9 and the roller 10 is performed by the grease composition, and the lubrication of the rolling bearing 4 is the same type or different type of grease from the roller clutch 5. Done by the composition.

  As shown in FIG. 1, the rolling bearing 4 includes sealing devices 4 a and 4 b such as seals, so that the grease composition sealed in the rolling bearing 4 is prevented from leaking from the rolling bearing 4. However, when the grease composition of the roller clutch 5 and the grease composition of the rolling bearing 4 are the same type, the sealing device 4b on the side facing the roller clutch 5 of the sealing devices 4a and 4b of the rolling bearing 4 is provided. It does not matter if it is not.

  The type of grease composition that lubricates the roller clutch 5 is not particularly limited, but contains a base oil, a thickener, and an additive. Below, the raw material of the grease composition which lubricates the roller clutch 5 is demonstrated in detail.

[About base oil]
As the base oil of the grease composition, for example, a mineral lubricating oil or a synthetic lubricating oil can be used. Examples of the mineral lubricating oil include paraffinic mineral oil, naphthenic mineral oil, and mixed lubricating oils thereof. Examples of the synthetic lubricating oil include synthetic hydrocarbon oil, ether oil, ester oil, and fluorine oil.

  Specific examples of the synthetic hydrocarbon oil include poly α-olefin oil, and specific examples of the ether oil include dialkyl diphenyl ether oil, alkyl triphenyl ether oil, and alkyl tetraphenyl ether oil. Specific examples of ester oils include diester oils, neopentyl type polyol ester oils, complex ester oils thereof, and aromatic ester oils. Furthermore, specific examples of the fluorine oil include perfluoroether oil, fluorosilicone oil, chlorotrifluoroethylene oil, and fluorophosphazene oil.

These base oils may be used individually by 1 type, and may be used in combination of multiple types suitably. In consideration of lubricating performance and life under high speed conditions, the base oil preferably contains a synthetic lubricating oil, particularly preferably a diester oil.
The kinematic viscosity at 40 ° C. of the base oil is preferably 20 to 150 mm ² / s. If it is less than 20 mm ² / s, the oil film becomes thin and the durability may be reduced, and if it exceeds 150 mm ² / s, the engagement of the roller clutch 5 may become a problem. In order to make such inconvenience more difficult to occur, the kinematic viscosity of the base oil at 40 ° C. is more preferably 25 to 90 mm ² / s.

[About thickener]
The type of the thickener is not particularly limited, and those generally used as the thickener of the grease composition can be used without any problem. For example, metal soaps such as lithium soap, calcium soap, sodium soap, aluminum soap, lithium complex soap, calcium complex soap, sodium complex soap, barium complex soap, and aluminum complex soap are listed.

In addition, organic compounds such as urea compounds (monourea, diurea, triurea, tetraurea, etc.), urethane compounds, sodium terephthalate compounds, and inorganic compounds such as bentonite and clay.
Of these thickeners, urea compounds are particularly preferred. In addition, a thickener may be used individually by 1 type, and may be used in combination of 2 or more types as appropriate.

  The penetration of the grease composition is preferably in the range of 250 to 340 at normal temperature (25 ° C.), and preferably in the range of 160 to 340 at −40 ° C. If the penetration at normal temperature is less than 250 and the penetration at -40 ° C is less than 160, there is a risk that the grease composition will not spread to the necessary parts when sliding mainly in the clutch part. Further, although the spring force is also used for engaging and releasing the roller 10 in the roller clutch 5, there is a possibility that the problem of worsening the movement of the spring 13 may occur. On the other hand, if the blending degree exceeds 340, there is a possibility that a problem such as the grease composition being liable to flow out due to vibration during driving of the automobile, for example.

[Additives]
In order to further improve various performances, various additives generally used in grease compositions may be added to the grease composition as necessary. Examples include extreme pressure agents, antioxidants, rust inhibitors, oiliness agents, and metal deactivators. These additives may be used alone or in combination of two or more. May be. The total content of additives is not particularly limited as long as the object of the present invention is not impaired.

  The type of extreme pressure agent is not particularly limited, and examples thereof include phosphorus extreme pressure agents, zinc dithiophosphate, and organic molybdenum. Specific examples include organic zinc compounds such as zinc dialkyldithiophosphate, zinc diaryldithiophosphate and zinc dialkyldithiocarbamate, and organic molybdenum compounds such as molybdenum dialkyldithiophosphate, molybdenum diaryldithiophosphate and molybdenum dialkyldithiocarbamate. Further, thiocarbamine compounds, phosphates, phosphites and the like can be mentioned.

Moreover, as an antioxidant, generally used antioxidants can be used without problems. Examples thereof include amine-based antioxidants such as phenyl-1-naphthylamine, phenol-based antioxidants such as 2,6-di-tert-dibutylphenol, sulfur-based antioxidants, and zinc dithiophosphate.
Furthermore, examples of the rust preventive include sulfonates such as alkali metals and alkaline earth metals. Examples thereof include alkyl succinic acid derivatives such as alkyl succinic acid esters and alkenyl succinic acid esters, alkenyl succinic acid derivatives, and partial esters of polyhydric alcohols such as sorbitan monooleate.

Furthermore, examples of the oily agent include fatty acids and animal and vegetable oils. Furthermore, examples of the metal deactivator include benzotriazole.
The manufacturing method of such a grease composition is not particularly limited, and can be prepared in the same manner as a conventionally known manufacturing method. For example, when a urea compound is used as a thickener, a grease composition is generally produced by reacting raw materials (amines and diisocyanate) of a diurea compound in a base oil. The production conditions (for example, temperature and stirring / mixing time) are appropriately set depending on the base oil to be used, the raw material of the diurea compound, additives, and the like. Further, after the additive is added, it is necessary to sufficiently stir and disperse it uniformly in the grease composition. In this case, heating is also effective.

  The grease composition produced as described above imparts low friction and low wear to the roller clutch 5 when the outer peripheral surface of the clutch inner ring 6 and the inner peripheral surface of the clutch outer ring 9 and the roller 10 slide. Reduces heat generation and wear of sliding contact parts due to friction of contact parts. In particular, the pressing of the roller 10 to the outer peripheral surface of the clutch inner ring 6 and the inner peripheral surface of the clutch outer ring 9 is not hindered even at a low temperature when the viscosity of the grease composition increases (fluidity decreases). Therefore, the roller clutch 5 can be reliably operated for a long time even at a low temperature (for example, −40 ° C.).

Furthermore, the grease composition used for lubricating the roller clutch 5 can be suitably used for lubricating the rolling bearing 4. Then, since the roller clutch 5 and the rolling bearing 4 can be lubricated with a common grease composition, the manufacturing and maintenance costs of the roller clutch built-in pulley device 1 can be reduced.
Further, in this pulley device 1 with a built-in roller clutch, the clutch inner ring 6 of the roller clutch 5 is made of a steel material having a high temperature hardness, and the steel material constituting the clutch inner ring 6 is a material constituting the clutch outer ring 9. The hardness Hv at 100 ° C. is higher than that of the material constituting the roller 10 and the hardness Hv at 100 ° C. is 700 or more. Therefore, even when the roller clutch 5 is used under high-temperature and high-speed conditions, wear and seizure hardly occur. Therefore, the roller clutch built-in pulley apparatus 1 has a long life even when used under high temperature and high speed conditions.

  Further, at least one of the clutch inner ring 6, the clutch outer ring 9 and the roller 10 of the roller clutch 5 is carbon 0.2 mass% or more and less than 0.6 mass%, silicon is 0.5 mass% or more and 2 mass% or more. It is preferable to use a steel material containing 0.5% by mass or more and less than 1% by mass of manganese, 1% by mass or more and less than 2% by mass of chromium, and 0.5% by mass or more and less than 2% by mass of molybdenum. And it is preferable that the member comprised with this steel material is carbonitriding, and the hardness Hv in 100 degreeC is 700 or more.

With such a configuration, the member is excellent in wear resistance and seizure resistance under high temperature and high speed conditions. Therefore, even when the roller clutch 5 is used under high temperature and high speed conditions, wear and seizure occur. Hateful. Therefore, the roller clutch built-in pulley apparatus 1 has a long life even when used under high temperature and high speed conditions.
In particular, the clutch inner ring 6 is preferably made of the steel material. In that case, the roller 10 is preferably made of bearing steel SUJ2. Then, the wear resistance and seizure resistance under high temperature and high speed conditions are particularly excellent.

Furthermore, if the roller clutch 5 is lubricated with a grease composition using ester oil as a base oil, the wear resistance and seizure resistance of the roller clutch 5 under high temperature and high speed conditions can be further improved.
The high temperature and high speed condition in the present invention means, for example, that the atmospheric temperature of the one-way clutch built-in type rotation transmission device is 100 ° C. or higher, or the temperature of the one-way clutch built-in type rotation transmission device is 120 ° C. or higher, and This means that the rotation speed of the built-in rotation transmission device is 7000 rpm or more.

  When such a roller clutch built-in type pulley device 1 is used as a device for rotationally driving an automobile engine accessory such as an alternator, the rotation shaft of the engine accessory such as an alternator is fitted and fixed to the sleeve 2. At the same time, an endless belt (not shown) is wound around the pulley 3 and a driving pulley (not shown) fixed to the end of the crankshaft of the engine. When the driving pulley is rotated, the pulley 3 is rotated by the endless belt, and the rotational force is transmitted to the sleeve 2 by the roller clutch 5. The portion of the outer peripheral surface of the pulley 3 that contacts the endless belt may be provided with irregularities as shown in FIG.

  However, when the rotational speed of the pulley 3 is the same as the rotational speed of the sleeve 2, that is, the endless belt is in an acceleration tendency or a constant speed state, and the speed is equal to or higher than the rotational speed of the rotating shaft of the engine accessory. In this case, the rotational force transmitted from the endless belt to the pulley 3 is transmitted to the rotational shaft of the engine accessory via the sleeve 2, but when the rotational speed of the sleeve 2 is slower than the rotational speed of the pulley 3, that is, When the endless belt tends to decelerate and its speed is slower than the rotational speed of the rotating shaft of the engine accessory, the rotational force is not transmitted from the pulley 3 to the sleeve 2.

  When the pulley device 1 with a built-in roller clutch is used as an engine accessory drive device at the time of idling stop of the engine, the crankshaft of the engine and the drive shaft of the electric motor are fitted and fixed to the sleeve 2, and the engine When the crankshaft or the drive shaft of the electric motor is rotationally driven, the rotational force is transmitted to the pulley 3 by the roller clutch 5. Of the crankshaft of the engine and the drive shaft of the electric motor, the one that is not rotationally driven is prevented from rotating. For example, when an engine auxiliary machine such as a compressor is rotationally driven by an electric motor when the engine is stopped, the drive shaft of the electric motor rotates and the crankshaft of the engine does not rotate.

In addition, this embodiment shows an example of this invention and this invention is not limited to this embodiment.
For example, in the present embodiment, the case where a deep groove ball bearing is used as the rolling bearing 4 has been described as an example. However, the one-way clutch built-in type rotation transmission device of the present invention includes various types of rolling bearings. It is possible to use. For example, radial rolling bearings such as angular contact ball bearings, self-aligning ball bearings, cylindrical roller bearings, tapered roller bearings, needle roller bearings, and self-aligning roller bearings, and thrust types such as thrust ball bearings and thrust roller bearings This is a rolling bearing.

The number of rolling bearings 4 is not particularly limited, and may be one or three or more.
Furthermore, in this embodiment, although the case where the roller clutch was used as a one-way clutch was illustrated and demonstrated, you may employ | adopt other types of one-way clutches, such as a sprag clutch and a cam clutch.

Further, the clutch inner ring 6 and the clutch outer ring 9 may be omitted, and the outer peripheral surface of the sleeve 2 or the inner peripheral surface of the pulley 3 may be used as the cam surface 8. That is, the roller 10 is disposed between the outer peripheral surface of the sleeve 2 and the inner peripheral surface of the pulley 3 and is engaged with both peripheral surfaces. In this case, the sleeve 2 also serves as the clutch inner ring 6, and the pulley 3 also serves as the clutch outer ring 9.
Further, the rotational force may be transmitted from the pulley 3 to the sleeve 2 as described above, but conversely may be transmitted from the sleeve 2 to the pulley 3.
Further, a gear may be used as the outer rotating member instead of the pulley 3.

〔Example〕
Hereinafter, the present invention will be described more specifically with reference to Examples and Comparative Examples. We prepared roller pulleys with built-in roller clutches for alternators with different types of materials constituting the clutch inner ring, clutch outer ring, and roller, and the types of grease compositions for lubricating the roller clutch, and evaluated their performance (life). The configuration of the evaluated pulley device with built-in roller clutch for the alternator is substantially the same as that of the pulley device with built-in roller clutch 1 of FIG. 1 except for the types of the material and the grease composition.

  The types of materials constituting the clutch inner ring, the clutch outer ring, and the roller are as shown in Table 1. Here, the steel material for high temperature is carbon 0.2 mass% or more and less than 0.6 mass%, silicon is 0.5 mass% or more and less than 2 mass%, manganese is 0.5 mass% or more and less than 1 mass%, It is a steel material containing chromium in an amount of 1% by mass to less than 2% by mass and molybdenum in an amount of 0.5% by mass to less than 2% by mass with the balance being iron and inevitable impurities. And the member comprised with this steel material for high temperature is carbonitrided, and the hardness Hv in 100 degreeC is set to 770.

The carbonitriding conditions were 3 hours at 800 to 950 ° C. in a mixed atmosphere of Rx gas and ammonia gas. And after carbonitriding, the tempering process was performed at 200-350 degreeC.
The hardness Hv of SUJ2 at 100 ° C. is 680, and the hardness Hv of SCM415 at 100 ° C. is 660.

  The grease composition for lubricating the roller clutch includes a base oil, a thickener, and an additive. The base oil is an ether oil or an ester oil, and its kinematic viscosity and content in the entire grease composition are as shown in Table 1. Further, the thickener is a diurea compound, and the content in the entire grease composition is as shown in Table 1. Further, amine-based antioxidants and zinc carboxylate are used as additives, and the content in the entire grease composition is as shown in Table 1.

These grease compositions were produced as follows. A predetermined amount of base oil and amine compound were charged into the reaction vessel and mixed while warming. Further, the same amount of base oil and 4,4′-diphenylmethane diisocyanate (manufactured by Tokyo Chemical Industry Co., Ltd.) were charged into another container and mixed while heating. When a mixture of this base oil and 4,4′-diphenylmethane diisocyanate is charged into the aforementioned reaction vessel and stirred, the reaction between amine and isocyanate proceeds to produce a diurea compound. Subsequently, the grease composition was obtained by adding the above-mentioned additive and processing with a three-stage roll mill.
The properties of these grease compositions, that is, the penetration at 25 ° C., the coefficient of friction, and the thermal stability are also shown in Table 1. In addition, the measuring method of a friction coefficient and thermal stability is as follows.

[Measurement method of friction coefficient]
The measurement of the friction characteristic (friction coefficient) was performed with a ball-on-disk tester. That is, a grease composition was applied onto a disk of a ball-on-disk tester, the ball was placed, and the ball was slid under conditions of a surface pressure of 2 GPa and a sliding speed of 0.2 m / s. Then, the coefficient of friction was measured 1 minute after the start of sliding.

[How to measure thermal stability]
The thermal stability was measured by a high temperature standing test. The grease composition was uniformly applied to a stainless steel petri dish made of SUS304 to a thickness of 3 mm, and left in a thermostat at 160 ° C. for 500 hours. The total acid value of the grease composition before and after standing was measured, and the increase amount of the total acid value was determined. 3 mgKOH / g or less was accepted.

  Next, a method for evaluating the alternator roller clutch built-in pulley apparatus will be described. The pulley device with a built-in roller clutch for the alternator was evaluated by a high-temperature high-speed engagement durability test. That is, the pulley device with a built-in roller clutch for an alternator was operated under high temperature and high speed conditions, and the time until the roller clutch was damaged due to wear or seizure and became inoperable was measured. The results are shown in Table 1. When the roller clutch was not damaged even after 900 hours, the test was terminated and “900 hours or more” is shown in Table 1.

The operating conditions are as follows.
Front bearing temperature: 140 ° C
Pulley rotation speed: 8000 ± 600rpm
Pulley load: 2000N
Alternator power generation: 150A
As can be seen from the results in Table 1, Examples 1 to 5 in which at least one of the clutch inner ring, the clutch outer ring, and the roller was made of the high-temperature steel material had a longer life than Comparative Examples 1 and 2. Moreover, it turns out that it becomes longer life by comprising a clutch inner ring | wheel with the said steel material for high temperature from the comparison of Examples 2-5. Furthermore, from the comparison of Examples 1 and 5, it can be seen that the former has a longer life in the grease composition based on the ester oil and the grease composition based on the ether oil.

DESCRIPTION OF SYMBOLS 1 Roller clutch built-in pulley apparatus 2 Sleeve 3 Pulley 4 Rolling bearing 5 Roller clutch 6 Clutch inner ring 9 Clutch outer ring 10 Roller

Claims (4)

An inner rotating member, an outer rotating member concentrically arranged around the inner rotating member, a rolling bearing disposed between the rotating members and supporting the rotating members in a relatively rotatable manner, and the rotating members A one-way clutch built-in type, comprising: a one-way clutch that is connected between the two rotating members and transmits only the rotational force that relatively rotates one of the two rotating members relative to the other in a predetermined direction. In the rotation transmission device,
The one-way clutch includes an inner clutch member fixed to the outer peripheral surface of the inner rotating member, an outer clutch member arranged concentrically around the inner clutch member and fixed to the inner peripheral surface of the outer rotating member, A plurality of engagement elements disposed between an outer peripheral surface of the inner clutch member and an inner peripheral surface of the outer clutch member; and an outer peripheral surface of the inner clutch member and an inner peripheral surface of the outer clutch member. By engaging the engagement element, the clutch members are connected to transmit the rotational force,
The inner clutch member is made of a steel material having a hardness Hv at 100 ° C. higher than that of the material constituting the outer clutch member and the engaging member and a hardness Hv at 100 ° C. of 700 or more. One-way clutch built-in type rotation transmission device.   At least one of the inner clutch member, the outer clutch member, and the engagement member is 0.2% by mass to less than 0.6% by mass of carbon, 0.5% by mass to less than 2% by mass of silicon, and manganese. It is composed of a steel material containing 0.5% by mass or more and less than 1% by mass, chromium by 1% by mass or more and less than 2% by mass, and molybdenum by 0.5% by mass or more and less than 2% by mass, and subjected to carbonitriding treatment. The one-way clutch built-in rotation transmission device according to claim 1, wherein the hardness Hv at 100 ° C. is 700 or more.   At least the inner clutch member among the inner clutch member, the outer clutch member, and the engagement element is 0.2% by mass or more and less than 0.6% by mass of carbon, and 0.5% by mass or more and less than 2% by mass of silicon. , Composed of a steel material containing 0.5 mass% to less than 1 mass% of manganese, 1 mass% to less than 2 mass% of chromium, and 0.5 mass% to less than 2 mass% of molybdenum, and carbonitriding The one-way clutch built-in rotation transmission device according to claim 1, wherein the hardness Hv at 100 ° C after the treatment is 700 or more.   The one-way clutch built-in type rotation according to any one of claims 1 to 3, wherein the lubricant that lubricates between the inner clutch member and the outer clutch member and the engagement element is grease. Transmission device.

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