JP2009180378A - Rolling bearing for rocker arm - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing for a rocker arm which can suppress the shortening of a life while being formed compact in size. <P>SOLUTION: The rolling bearing 50 for the rocker arm comprises a roller 4, a roller shaft 2, and rollers 3 all having nitrogen enriched layers. The grain size number of austenite crystal grains of the nitrogen enriched layer of a member of each of the roller shaft 2 and the roller 3 is in a range exceeding No.10, a remaining austenite amount is 11-25 vol.%, and a nitrogen content is 0.1-0.7 mass%. The grain size number of the austenite crystal grains of the nitrogen enriched layer of the roller 4 is smaller than the grain size number of the austenite crystal grains of the nitrogen enriched layer of the member of each of the roller shaft 2 and the roller 3, and the remaining austenite amount of the nitrogen enriched layer of the roller 4 is larger than the remaining austenite amount of the nitrogen enriched layer of the member of each of the roller shaft 2 and the roller 3. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a rocker arm rolling bearing used for opening and closing an intake valve and an exhaust valve of an automobile engine. More specifically, the present invention relates to a rocker arm rolling bearing capable of suppressing a reduction in life while achieving compactness. It relates to bearings.

  Some recent rolling bearings, such as rolling bearings used for rocker arms used to open and close engine intake valves and exhaust valves, are full-roller type bearings that are used for high-speed, high-load applications. There are many. In particular, in a full-roller type bearing without a cage, the rollers are likely to be skewed due to interference between the rollers or because the roller position is not controlled smoothly. Moreover, if the lubricating oil is not supplied well into the bearing, a situation where the lubricating condition is poor is likely to occur. As a result, sliding heat generation and local surface pressure increase occurred, and surface damage (peeling, smearing, surface-origin separation) and internal origin-type delamination were likely to occur despite a large load capacity in the calculation. .

  In applications where the outer diameter of the outer ring is in rolling contact with the cam, such as rolling bearings used for rocker arms used to open and close engine intake valves and exhaust valves, the conventional method has been mainly aimed at improving the outer diameter of the outer ring. There were many improvements. For example, compressive residual stress due to processing such as shot peening, and long life due to high hardness (machining effect) due to high-concentration carbonitriding have been performed mainly to improve the outer diameter of the outer ring that is in rolling contact with the mating cam. .

In the conventional technology so far, the following measures have been taken.
(1) A bearing component in which shot peening is applied to the bearing ring of the bearing component in order to improve the rolling fatigue life, and a reinforcing layer, a retained austenite-containing layer, and a hardened hardening layer are sequentially provided from the surface to the inside (Patent Document 1).

  (2) A technique for efficiently adjusting the size, area ratio, retained austenite amount and hardness of carbide in the martensite structure by shot peening (Patent Document 2).

  (3) Technology for matching the peak height and distribution of residual compressive stress due to shot peening to the maximum shear stress and depth of action acting during use in order to improve rolling fatigue life (Patent Document 3).

  (4) In carburized bearings, the combination of residual compressive stress σ (MPa) and residual austenite γ (%) on the surface after shot peening is performed to extend the life and final surface finishing is performed. A control method that satisfies 001σ + 0.3γ ≧ 1.0.

  (5) A cam follower device in which the hardness of the outer diameter of the cam follower outer ring is equal to that of the counterpart cam, and the hardness of the inner diameter of the outer ring is higher than the hardness of the outer diameter (Patent Document 4).

(6) In a component that is in rolling contact or rolling and sliding contact with other components facing each other, the maximum compressive stress of the surface layer portion having a depth of 0 to 50 μm from the surface is 50 to 110 kgf / mm ² , and the hardness is HV 830 to 960, The residual austenite is 7% or more, the average wavelength of the surface roughness is 25 μm or less, and these are achieved by shot peening (Patent Document 5).

  Although there are few improvements to extend the rolling life of the roller shaft, rollers, and the entire bearing corresponding to the inner ring, as shown below, heat resistance and microstructure stability by carbonitriding are given, and hardness is increased, as shown below There is an example in which the life of the bearing is extended by the above.

  (D1) A bearing for a cam follower device for a valve operating mechanism of an engine having a calculated service life of 1000 hours or more at a rated engine speed (Patent Document 6).

  (D2) Carbide ratio: 10 to 25%, decomposition ratio with respect to initial value of retained austenite: 1/10 to 3/10, end surface hardness: HV830 to 960, average wavelength of surface roughness: 25 μm or less Bearing steel is carbonitrided and hard shot peened to realize a bearing shaft (Patent Document 7).

  (D3) A cam follower shaft in which a solid lubricating film such as a polymer compound is formed on the shaft in order to improve the wear resistance of the shaft (Patent Document 8).

  (D4) A cam follower shaft made of tool steel or the like and made hard by ion nitriding or ion plating at a temperature lower than the tempering temperature (Patent Document 9).

  (D5) A bearing for a cam follower device for a valve operating mechanism of an engine in which a bending stress with respect to the shaft is 150 MPa or less (Patent Document 10).

  (D6) A cam follower for a valve operating mechanism of an engine in which a phosphate film having excellent lubricating oil retention is attached to the rolling surface of a bearing component (Patent Document 11).

  (D7) A cam follower for a valve operating mechanism of an engine having a crowned roller rolling region (Patent Document 12).

  (D8) Carburized shaft with high-concentration carburizing treatment or carbonitriding treatment in which the carbon concentration of the surface of the rolling surface of the shaft is 1.2% to 1.7% C, and the internal hardness is HV300 (Patent Document 13) .

Japanese Patent Laid-Open No. 2-168022 JP 2001-65576 A Japanese Patent Laid-Open No. 3-199716 Japanese Utility Model Publication No. 3-119508 Japanese Patent No. 3125434 JP 2000-38907 A Japanese Patent Laid-Open No. 10-47334 Japanese Patent Laid-Open No. 10-103339 JP-A-10-110720 JP 2000-38906 A JP 2002-3212 A Japanese Utility Model Publication No. 63-185917 JP 2002-194438 A

  In recent years, the valve mechanism has been increasingly complicated by adopting a variable valve lift amount mechanism and a variable valve timing mechanism. Further, there is a demand for weight reduction of movable parts and the engine itself. For these reasons, the space occupied by the rocker arm in the valve mechanism has been limited. For this reason, the rolling bearing incorporated in the rocker arm is also required to be more compact than before.

  However, if the rolling bearing for the rocker arm is made compact, the load applied per unit area increases, so there is a problem that the life is shortened. For this reason, it was not possible to suppress a reduction in the service life while reducing the size of the rocker arm rolling bearing.

  Accordingly, an object of the present invention is to provide a rocker arm rolling bearing capable of suppressing a reduction in life while achieving compactness.

  The rocker arm rolling bearing of the present invention includes an outer ring that is in rolling contact with the cam of the engine, an inner ring that is positioned inside the outer ring and is fixed to the rocker arm, and a plurality of rolling elements that are interposed between the outer ring and the inner ring. In the rocker arm rolling bearing provided with the outer ring, the inner ring, and the rolling elements all have a nitrogen-enriched layer. The grain size number of the austenite grains in the nitrogen-enriched layer in both the inner ring and the rolling element is in the range exceeding 10 and the amount of retained austenite in the nitrogen-enriched layer in the member is 11% by volume or more and 25% by volume or less. And the nitrogen content of the nitrogen-enriched layer in the member is 0.1% by mass or more and 0.7% by mass or less. Furthermore, the particle size number of the austenite crystal grains of the nitrogen-enriched layer in the outer ring is smaller than the particle size number of the austenite crystal grains of the nitrogen-enriched layer in both members, and the amount of retained austenite of the nitrogen-enriched layer in the outer ring is More than the amount of retained austenite in the nitrogen-enriched layer in both members.

  By reducing the austenite grains of both the inner ring and the rolling elements as the particle size number exceeds 10, the rolling fatigue life can be greatly improved. When the particle size number of the austenite particle size is 10 or less, the rolling fatigue life is not greatly improved. Usually, it should be 11 or more. The average crystal grain size may be 6 μm or less. Although it is desirable that the austenite particle size is finer, it is usually difficult to obtain a particle size number exceeding # 13. The austenite crystal grain size may be obtained by an ordinary method defined in JIS, or may be converted by obtaining an average grain size corresponding to the crystal grain size number by an intercept method or the like.

  Note that the austenite crystal grains do not change even in the surface layer portion where the nitrogen-enriched layer exists or in the inner part thereof. Therefore, the target position of the above crystal grain size number range is the surface layer portion and the inside. Here, the austenite crystal grains are crystal grains of austenite that has undergone phase transformation during quenching heating, and this means what remains as a past history even after transformation to martensite by cooling. .

  In addition, when the amount of retained austenite is less than 11% volume, the surface damage life tends to be greatly reduced. When the amount of retained austenite is more than 25% by volume, the amount of retained austenite is different from that obtained by performing normal carbonitriding. Since it will disappear, the aging change will worsen.

  The amount of retained austenite is a value at the surface layer of 50 μm of the rolling surface after grinding, and can be measured, for example, by comparing the diffraction intensities of martensite α (211) and retained austenite γ (220) by X-ray diffraction. it can. In addition, using the fact that the austenite phase is a non-magnetic material and the ferrite phase is a ferromagnetic material, it can also be measured by determining the magnetizing force with a magnetic balance or the like. In addition, it can measure easily using a commercially available measuring apparatus.

  The nitrogen-enriched layer is a layer having an increased nitrogen content formed on the surface layer, and can be formed by a process such as carbonitriding, nitriding, or nitriding. When the nitrogen content of the nitrogen-enriched layer is less than 0.1% by mass, there is no effect, and in particular, the surface damage life is reduced. When the nitrogen content is more than 0.7% by mass, voids called voids are formed, or the retained austenite increases too much, resulting in a short life. The nitrogen content of the nitrogen-enriched layer is a value at the surface layer of 50 μm of the rolling surface after grinding, and can be measured by, for example, EPMA (Electron Probe Micro-Analysis: wavelength dispersion type X-ray microanalyzer).

  As described above, according to the rolling bearing for a rocker arm of the present invention, a long life can be realized. Therefore, the life of the bearing is not lowered compared with the conventional one even if it is made compact. Therefore, it is possible to suppress a reduction in life while achieving compactness.

  (C1) The rocker arm is attached to a rocker arm shaft positioned between one end and the other end, and the end of the valve for opening and closing the engine is in contact with one end, and the rocker arm May have a bifurcated inner ring support at the other end, and the inner ring of the rocker arm rolling bearing of the present invention may be fixed to the bifurcated inner ring support.

  (C2) The rocker arm rolling bearing of the present invention is provided between one end and the other end of the rocker arm, and the inner ring is fixed to the inner ring hole extending between the two side walls of the rocker arm. The end of the valve for opening and closing the engine may be in contact with one end of the rocker arm, and the pivot may be in contact with the other end of the rocker arm.

  Furthermore, (c3) the rocker arm includes a rocker arm body and an interlocking rod that transmits stress from the cam, and the rocker arm body is between one end and the other end of the rocker arm body. The end of the valve for engine opening / closing comes into contact with one end of the rocker arm main body, and one end of the interlocking rod comes into contact with one end of the rocker arm main body. The inner ring of the rocker arm rolling bearing of the present invention may be fixed to the other end of the interlocking rod.

  The rocker arms (c1), (c2), and (c3) described above are common in that the driving force from the cam is transmitted to the engine valve, but the structure is different and can correspond to different engine types. It is like that.

  In the present specification, the “inner ring” includes a solid shaft and a hollow shaft.

  According to the rolling bearing for a rocker arm of the present invention, it is possible to suppress a reduction in life while achieving compactness.

It is a schematic front view which shows the use condition of the rolling bearing for rocker arms in one embodiment of this invention. It is sectional drawing which follows the II-II line in FIG. It is a schematic front view which shows the use condition of the rolling bearing for rocker arms in other embodiment of this invention. It is a schematic front view which shows the use condition of the rolling bearing for rocker arms in another embodiment of this invention. It is the figure which expanded the part containing the rolling bearing for rocker arms of FIG. It is a figure explaining the heat processing method in one embodiment of this invention. It is a figure explaining the modification of the heat processing method in one embodiment of this invention. It is a figure which shows the microstructure of a bearing component, especially an austenite grain. (a) is a bearing part of the example of the present invention, and (b) is a conventional bearing part. (A) shows the austenite grain boundary illustrated in FIG. 8 (a), and (b) shows the austenite grain boundary illustrated in FIG. 8 (b). It is sectional drawing which shows the structure (dimension) of Sample 1 to Sample 6. It is sectional drawing which shows the structure (dimension) of the sample 7-11. It is a front view which shows the principal part of a peeling lifetime test apparatus. It is sectional drawing along the XIII-XIII line | wire of FIG.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a schematic front view showing a usage state of a rocker arm rolling bearing according to an embodiment of the present invention, and FIG. 2 is a sectional view taken along line II-II in FIG. 1 and 2, the rocker arm 1 is rotatably supported by the rocker arm shaft 5 via a bearing metal or the like at the center.

  An adjustment screw 7 is screwed into one end 1 b of the rocker arm 1. The adjustment screw 7 is fixed by a lock nut 8 and is in contact with an upper end portion 9a of a valve 9 of an intake valve or an exhaust valve of the internal combustion engine at a lower end thereof. The valve 9 is biased by the elastic force of the spring 10.

  The rocker arm 1 integrally has an inner ring support portion 14 formed in a bifurcated shape at the other end 1a. Both ends of the roller shaft 2 corresponding to the inner ring are caulked in the roller shaft hole opened in the bifurcated inner ring support portion 14 and fixed by press-fitting or retaining rings. A roller 4 constituting an outer ring is supported at the center of the outer peripheral surface of the roller shaft 2 via a plurality of rollers 3 as rolling elements. That is, a plurality of rollers 3 are interposed between the roller shaft 2 and the roller 4. The axial direction of the roller 3 is arranged parallel to the axis of the roller shaft 2. The outer peripheral surface of the roller 4 is in contact with the cam surface of the cam 6 provided on the cam shaft by the urging force of the spring 10. In other words, the cam 6 and the roller 4 are in rolling contact.

  When the cam 6 rotates, it is pushed by the cam 6 and the rocker arm 1 swings up and down. This swing is transmitted to the valve 9 with the rocker arm shaft 5 as a fulcrum, and the valve 9 opens and closes. The rocker arm rolling bearing 50 according to the present embodiment is a full roller bearing in which no cage is used, and includes a roller shaft 2, a plurality of rollers 3, and a roller 4. The rocker arm rolling bearing 50 plays a role of reducing friction between the rocker arm 1 and the cam 6 and improving wear resistance. Since the rocker arm rolling bearing 50 rotates while being in contact with the cam 6, the pressing force and impact force of the cam 6 act on the roller 4.

  FIG. 3 is a schematic front view showing a usage state of a rocker arm rolling bearing according to another embodiment of the present invention. Referring to FIG. 3, a rocker arm rolling bearing 50 is provided between one end 1 b and the other end 1 a of the rocker arm 1. A roller shaft hole (not shown) as an inner ring hole is formed between the two side walls 1 c of the rocker arm 1. The roller shaft 2 is fixed to the roller hole. Further, an upper end 9 a of an engine opening / closing valve 9 is in contact with one end 1 b of the rocker arm 1, and a pivot hole 15 is provided at the other end 1 a of the rocker arm 1. The pivot hole 15 abuts on a pivot (not shown). The rocker arm 1 provided with the pivot hole 15 is biased by a spring 10 in a predetermined direction around the pivot. The driving force transmitted from the cam 6 is received by the roller 4 to move the valve 9 against the urging force of the spring 10.

  FIG. 4 is a schematic front view showing a usage state of a rocker arm rolling bearing according to still another embodiment of the present invention. FIG. 5 is an enlarged view of a portion including the rocker arm rolling bearing of FIG.

  Referring to FIGS. 4 and 5, rocker arm main body 11 and interlocking bar 16 that transmits stress from cam 6 are provided. A rocker arm shaft 5 is disposed between one end portion 11b and the other end portion 11a of the rocker arm main body 11, that is, at the central portion of the rocker arm main body 11, and the rocker arm main body 11 rotates around it. . The upper end portion 9 a of the valve 9 is in contact with one end portion 11 b of the rocker arm body 11, and the valve 9 is biased by the elastic force of the spring 10. Further, the upper end portion 16 b of the interlocking rod 16 is in contact with the other end portion 11 a of the rocker arm main body 11. The adjustment screw 7 has a function of adjusting the contact position between the rocker arm body 11 and the interlocking rod 16. The roller shaft 2 of the rocker arm rolling bearing 50 is attached to the hollow bearing mounting portion 16 a located at the lower end portion of the interlocking rod 16 by the mounting member 17. The cam 6 abuts against the roller 4 of the rocker arm rolling bearing 50 and transmits the driving force to the interlocking rod 16.

  1 to 5, there is no particular distinction between one and the other, and only an end that will be described earlier in the order of description is merely one end.

  Of the members constituting the rocker arm rolling bearing 50, all of the roller 4, the roller shaft 2, and the roller 3 have a nitrogen-enriched layer. Further, at least one member of the roller shaft 2 and the roller 3 is subjected to a heat treatment by a low-temperature secondary quenching method to be described below, whereby the nitrogen-enriched layer of at least one member of the roller shaft 2 and the roller 3 The grain size number of the austenite crystal grains is in the range exceeding No. 10, the residual austenite amount is 11% by volume or more and 25% by volume or less, and the nitrogen content is 0.1% by mass or more and 0.7% by mass or less. .

Next, heat treatment including carbonitriding performed on at least one bearing component of the inner ring (roller shaft 2) and rolling element (roller 3) of the rolling bearing will be described. FIG. 6 is a diagram for explaining a heat treatment method according to an embodiment of the present invention. Moreover, FIG. 7 is a figure explaining the modification of the heat processing method in one embodiment of this invention. Figure 6 is a heat treatment pattern showing a method of performing primary quenching and secondary quenching, FIG. 7 is a material in the course quenching cooled to below the A ₁ transformation point temperature, then Ru finally quenched by reheating method It is the heat processing pattern which shows. Both are exemplary embodiments of the present invention. In these figures, it was sufficiently the penetration of addition of carbon to diffuse carbon and nitrogen in the matrix of the treated T ₁ steel is cooled below the A ₁ transformation point. Next, in the process T ₂ of the in the figure, than the processing T ₁ is reheated to a low temperature, subjected to oil quenching from there.

  Rather than performing normal quenching, that is, carbonitriding once after the carbonitriding treatment, the crack strength can be improved and the aging change rate can be reduced while carbonitriding the surface layer portion. As described above, according to the above heat treatment method, it is possible to obtain a microstructure in which the grain size of austenite crystal grains is ½ or less of the conventional one. The bearing parts subjected to the above heat treatment have a long rolling fatigue characteristic, can improve the cracking strength, and can also reduce the rate of dimensional change over time.

  FIG. 8 is a view showing the microstructure of the bearing part, particularly austenite grains. FIG. 8A shows a bearing part of the present invention example, and FIG. 8B shows a conventional bearing part. That is, FIG. 8A shows the austenite grain size of the bearing steel to which the heat treatment pattern shown in FIG. 6 is applied. For comparison, FIG. 8B shows the austenite grain size of the bearing steel obtained by the conventional heat treatment method. FIGS. 9A and 9B are diagrams showing the austenite grain boundaries illustrated in FIGS. 8A and 8B. From the structure showing the austenite crystal grain size, the conventional austenite grain size is a JIS standard grain size number of 10 or less, and according to the heat treatment method of the present invention, the 12th fine grain can be obtained. Moreover, the average particle diameter of Fig.8 (a) was 5.6 micrometers as a result of measuring by the intercept method.

Examples of the present invention will be described below.
A roller, a roller shaft, and a roller of a rolling bearing for a rocker arm were manufactured using three types of heat treatment methods: standard heat treatment, carbonitriding treatment, and heat treatment of the present invention. The standard heat treatment, carbonitriding treatment, and heat treatment of the present invention referred to here are the following heat treatment methods.

  Standard heat treatment: After heating in RX gas atmosphere at a heating temperature of 840 ° C. and a holding time of 20 minutes, quenching was performed, followed by tempering at 180 ° C. for 90 minutes.

  Carbonitriding: Heating is performed at a temperature of 850 ° C. and a holding time of 150 minutes in an atmosphere of a mixed gas of RX gas and ammonia gas, followed by quenching from a temperature of 850 ° C. and then tempering at 180 ° C. for 90 minutes. Was done.

  Heat treatment of the present invention: Carbonitriding was performed under conditions of carbonitriding temperature 850 ° C. and holding time 150 minutes. During the carbonitriding process, an atmosphere of a mixed gas of RX gas and ammonia gas was used. Thereafter, according to the heat treatment pattern shown in FIG. 6, primary quenching is performed from a carbonitriding temperature of 850 ° C., followed by secondary quenching by heating at a temperature 800 ° C. lower than the carbonitriding temperature, and then at 180 ° C. Tempering was performed for 90 minutes.

  Table 1 shows the materials of the members obtained by these heat treatment methods.

Next, the material investigation method will be described.
(1) Austenite crystal grain size: The austenite crystal grain size was measured based on the JIS G 0551 steel austenite grain size test method.

  (2) Amount of retained austenite: The amount of retained austenite was measured by comparing the diffraction intensities of martensite α (211) and retained austenite γ (220) by X-ray diffraction. As the amount of retained austenite, the value at the surface layer of 50 μm of the rolling surface after grinding was adopted.

  (3) Nitrogen content: The nitrogen content was measured using EPMA. For the nitrogen content, the value at the surface layer of 50 μm of the rolling surface after grinding was adopted.

Next, the test results shown in Table 1 will be described.
(1) Austenite crystal grain size: The heat-treated member of the present invention is remarkably refined with a crystal grain size number of 12. The standard heat treatment member and the carbonitriding member have a crystal grain size number of 9 and 8, and are austenite crystal grains coarser than the heat treatment member of the present invention.

  (2) Residual austenite amount: The heat-treated member of the present invention has a residual austenite amount of 21% by volume, and appropriate austenite exists. The standard heat-treated member has a residual austenite amount of 7% by volume and is smaller than the heat-treated member of the present invention. Further, the carbonitrided member has a residual austenite amount of 29% by volume, which is larger than the heat-treated member of the present invention. From the above, it can be seen that the heat-treated member of the present invention is the amount of retained austenite between the standard heat-treated member and the carbonitrided member.

  (3) Nitrogen content: The nitrogen content of the heat-treated member of the present invention is 0.30%. Since the standard heat-treated member was not carbonitrided, the nitrogen content was 0%. Moreover, the nitrogen content of the carbonitriding member was 0.31%. The nitrogen content of the heat-treated member of the present invention tended to be slightly lower than the nitrogen content of the carbonitrided member. This is probably because the heat treatment of the present invention performs secondary quenching at a temperature of 800 ° C. lower than the carbonitriding temperature after the carbonitriding treatment.

  Subsequently, a roller, a roller shaft, and a roller manufactured by using the above-described three kinds of heat treatment methods were combined in various combinations to manufacture rocker arm rolling bearings, which were designated as Sample 1 to Sample 11. Among these, FIG. 10 shows a cross-sectional view showing the structures (dimensions) of Sample 1 to Sample 6, and FIG. 11 shows a cross-sectional view showing the structures (dimensions) of Sample 7 to Sample 11. As shown in FIG. 10, for Sample 1 to Sample 6, the width of the roller 4 and the roller 3 was 6.9 mm, and the width of the roller shaft 2 was 17.3 mm. On the other hand, as shown in FIG. 11, with respect to Sample 7 to Sample 11, the width of the roller 4 and the roller 3 was 5.5 mm, and the width of the roller shaft 2 was 15.9 mm. That is, Samples 7 to 11 were downsized by about 20% compared to Samples 1 to 6.

  Next, a peeling life test was performed on Sample 1 to Sample 11 by the following method. 12 is a front view showing a main part of the peel life test apparatus, and FIG. 13 is a cross-sectional view taken along line XIII-XIII in FIG. As shown in FIG. 12 and FIG. 13, the rocker arm rolling bearing 50 is arranged so that the drive roll 101 and the roller 4 of the peeling life test apparatus are in contact with each other, and the roller shaft 2 is fixed. And the roller 4 was rotated by rotating the drive roll 101 in the arrow direction in FIG. 12 in the state which applied the radial load from the drive roll 101 of the peeling life test apparatus to the rolling bearing 50 for rocker arms. The time (life) until peeling occurred in any of the roller 4, the roller shaft 2, and the roller 3 was measured. The load applied from the drive roll 101 to the rocker arm rolling bearing 50 was 2.58 kN, and the rotation speed of the roller 4 was 7000 r / min. Further, 10W-30 engine oil was used as the lubricating oil between the roller and the roller and the roller shaft, and the temperature of the lubricating oil was set to 100 ° C.

  Tables 2 and 3 show the combination of members in each sample and the peeling life of each sample. The products of the present invention are Sample 6, Sample 9, Sample 10, and Sample 11. The peel life of each sample is expressed as a ratio when the peel life of sample 1 is 1.

  As shown in Table 2, the sample 6 in which the heat treatment of the present invention was performed on all the members of the roller, the roller shaft, and the roller had a peeling life 3.5 times longer than the sample 1 in which the standard heat treatment was performed on all the members. It can be seen that Further, as shown in Table 3, sample 9 in which the roller and roller shaft were subjected to carbonitriding and the roller was subjected to the heat treatment of the present invention was 1. It can be seen that the peel life is twice as long. Further, it can be seen that the sample 10 obtained by subjecting the roller and the roller to carbonitriding and performing the heat treatment of the present invention on the roller shaft has a peeling life 1.5 times that of the sample 1. Furthermore, it can be seen that Sample 11 obtained by subjecting the roller to carbonitriding and performing the heat treatment of the present invention on the roller and roller shaft has a peel life 1.7 times that of Sample 1. From the above results, the roller, the roller shaft, and the roller all have a nitrogen-enriched layer, and the heat treatment of the present invention is performed on at least one member of the roller shaft and the roller, thereby reducing the size of the bearing. It can be seen that the reduction of the lifetime can be suppressed while planning.

  It should be understood that the embodiments and examples disclosed herein are illustrative and non-restrictive in every respect. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  1 rocker arm, 1a, 1b rocker arm end, 1c side wall, 2 roller shaft, 3 rollers, 4 rollers, 5 rocker arm shaft, 6 cam, 7 adjustment screw, 8 lock nut, 9 valve, 9a valve upper end, 10 Spring, 11 Rocker arm body, 11a, 11b Rocker arm body end, 14 Inner ring support, 15 Pivot hole, 16 Interlocking rod, 16a Bearing mounting portion, 16b Interlocking rod upper end, 17 Mounting member, 50 Roller bearing for rocker arm 101 drive roll.

Claims (4)

An outer ring in rolling contact with the engine cam;
An inner ring located inside the outer ring and fixed to the rocker arm;
In a rocker arm rolling bearing comprising a plurality of rolling elements interposed between the outer ring and the inner ring,
The outer ring, the inner ring, and the rolling elements all have a nitrogen-enriched layer,
The particle number number of the austenite crystal grains of the nitrogen-enriched layer in both the inner ring and the rolling element is in the range exceeding 10 and the amount of retained austenite of the nitrogen-enriched layer in the member is 11% by volume or more. 25% by volume or less, and the nitrogen content of the nitrogen-enriched layer in the member is 0.1% by mass or more and 0.7% by mass or less,
The austenite grain size number of the nitrogen-enriched layer in the outer ring is smaller than the austenite grain size number of the nitrogen-enriched layer in both members, and the amount of residual austenite of the nitrogen-enriched layer in the outer ring Is a rocker arm rolling bearing that is greater than the amount of retained austenite in the nitrogen-enriched layer in both members.   The rocker arm is attached to a rocker arm shaft positioned between one end and the other end, the end of the valve for opening and closing the engine contacts the one end, and the rocker arm is The rolling bearing for a rocker arm according to claim 1, wherein the other end portion has a bifurcated inner ring support portion, and the inner ring is fixed to the bifurcated inner ring support portion. Provided between one end of the rocker arm and the other end;
The inner ring is fixed to an inner ring hole extending between two side walls of the rocker arm, the end of the opening / closing valve of the engine abuts on one end of the rocker arm, and the other end of the rocker arm The rolling bearing for a rocker arm according to claim 1, wherein the pivot abuts.   The rocker arm has a rocker arm main body and an interlocking rod that transmits stress from the cam, and the rocker arm main body is located between one end and the other end of the rocker arm main body. An end portion of the valve for opening and closing the engine is in contact with the one end portion of the rocker arm body, and is attached to the rocker arm shaft, and one end portion of the interlocking rod is in contact with the other end portion of the rocker arm body. The rocker arm rolling bearing according to claim 1, wherein the inner ring is fixed to the other end of the interlocking rod.