JP5854898B2 - Sliding member - Google Patents

Description

  The present invention relates to a sliding member.

  A sliding member such as a sliding spline shaft used for a propeller shaft or the like is required to slide smoothly. It is known that stick slip is likely to occur when the dynamic friction coefficient is lower than the static friction coefficient, that is, when the friction coefficient and speed characteristics (μ-V characteristics) have a negative gradient. In order to solve this problem, Japanese Patent Application Laid-Open No. 2007-177955 (Patent Document 1) describes that a diamond-like carbon (DLC) film is applied to the surface of the sliding member.

JP 2007-177955 A

However, the diamond-like carbon coating process is expensive, so a reduction in cost is desired.
This invention is made | formed in view of such a situation, and it aims at providing the sliding member which can reduce generation | occurrence | production of a stick slip at low cost.

  (Claim 1) The sliding member of the present invention is a sliding member having a coating on the surface and sliding in the presence of a lubricant, and the coating comprises, as a binder, an epoxy resin and a phenol resin, The solid lubricant includes at least one disulfide of molybdenum disulfide and tungsten disulfide, polytetrafluoroethylene (PTFE), and polyethylene.

(Claim 2) Preferably, the mass ratio of the epoxy resin and the phenol resin is 25 to 100 parts by mass of the phenol resin with respect to 100 parts by mass of the epoxy resin, and the mass ratio of the polyethylene to the entire coating film is 5 to 10% by mass.
(Claim 3) Preferably, the lubricant contains a polyalphaolefin (PAO) as a base oil.
(Claim 4) Preferably, the 40 ° C. kinematic viscosity of the base oil is 1,000 mm ² / s or more.
(Claim 5) Preferably, the sliding member is a spline shaft that slides in an axial direction.

(Claim 1) By using a resin film instead of a DLC film as in the present invention, processing in the atmosphere is possible, and cost reduction can be achieved. The solid lubricant constituting the resin film contains disulfide, PTFE and polyethylene. Furthermore, a mixture of an epoxy resin and a phenol resin is used as a binder for the resin film. As a result, even if the number of repetitions increases, an increase in the static friction coefficient can be suppressed, and a decrease in the dynamic friction coefficient can be suppressed. That is, the state where the difference between the static friction coefficient and the dynamic friction coefficient is small can be maintained. Therefore, the occurrence of stick-slip can be continuously suppressed over a long period. In particular, wear resistance and toughness can be sufficiently exhibited by a mixture of an epoxy resin and a phenol resin as a coating binder.
(Claim 2) By making the mass ratio of the epoxy resin and the phenol resin and the mass ratio of the polyethylene with respect to the entire coating film as described above, the above-mentioned effect can be surely exhibited.

  (Claim 3) By using the lubricant, the static friction coefficient can be reduced, and the dynamic friction coefficient can be kept relatively large. As a result, even in the initial state, even when the number of repetitions increases, the μ-V characteristic can be a positive slope. Therefore, stick slip can be reliably suppressed over a long period of time. Furthermore, even if the number of repetitions is increased by the coating film and the lubricant, the static friction coefficient and the dynamic friction coefficient can be maintained in a small state. Therefore, the occurrence of stick slip can be suppressed. The reason why the above effect is achieved is considered as follows. In polyethylene used as a solid lubricant for coating, long molecular chains are entangled in particles. The molecular structure of polyethylene in the coating is similar to the molecular structure of PAO used as the base oil for the lubricant. For this reason, it is considered that PAO becomes familiar with the polyethylene in the coating, and PAO is infiltrated into the polyethylene particles.

(Claim 4) By using a base oil having a high kinematic viscosity that falls within this range, PAO soaked in the polyethylene particles in the coating forms a strong oil film, and it is difficult for the oil film to break. As a result, it is easy to maintain the state of the lubricant retained by the coating. Thereby, the said effect can be exhibited more effectively.
(Claim 5) Further, by applying the present invention to a spline shaft that slides in the axial direction, the occurrence of stick-slip when sliding in the axial direction can be suppressed.

It is an axial sectional view of a sliding spline shaft in the present embodiment. It is a radial direction partial expanded sectional view of the male spline of the sliding-type spline shaft of FIG. 3 shows a flowchart of a method for forming the male spline coating of FIG. FIG. 3 shows a schematic enlarged cross-sectional view of the male spline coating of FIG. 2. The relationship between the number of repetitions in the durability test and μs / μd is shown. The static friction coefficient of the sliding member according to the kind of lubricant base oil is shown. The static friction coefficient of the sliding member according to a polyethylene ratio is shown. The static friction coefficient of the sliding member according to the mass ratio of the solid lubricant with respect to the binder is shown. The friction coefficient with respect to the sliding speed in Example 1 is shown. The friction coefficient with respect to the sliding speed in a comparative example is shown. The friction coefficient with respect to the sliding speed in another comparative example is shown.

  A sliding spline shaft will be described as an example of the sliding member of this embodiment. However, the sliding member of the present invention can be effectively applied to all sliding members that can generate stick-slip in addition to the sliding spline shaft. The sliding spline shaft is applied to, for example, an automobile propeller shaft.

  As shown in FIG. 1, the sliding spline shaft includes a first shaft member 10 having a male spline 11 and a second shaft member 20 having a female spline 21. The male spline 11 is spline-fitted with the female spline 21 and is slidable in the axial direction. With such a configuration, the members 10 and 20 can transmit torque to each other and can be relatively moved in the axial direction. Here, grease as a lubricant is present at the spline sliding portion.

  The base material 16 of the male spline 11 is formed by forging, quenching, and tempering a steel material. In the present embodiment, the steel material forming the male spline 11 is, for example, S30C. In this embodiment, although the male spline 11 is formed by S30C, if it is steel materials or a metal material, it will not restrict to this.

  A base layer 17 and a coating 18 are formed on the surface of the male spline 11. That is, the base layer 17 is formed on the surface of the base material 16 made of steel, and the coating film 18 that is the surface layer is formed on the surface of the base layer 17. A dry film in which a resin is used as a binder and a solid lubricant is blended is applied to the film 18. Thus, the cost can be reduced by applying a dry film that is a resin film instead of a DLC film.

  Here, in this embodiment, the female spline 21 is formed of a steel material, for example, S30C. In the present embodiment, the female spline 21 is formed of S30C, but is not limited thereto as long as it is a steel material or a metal material. The coating 18 of the male spline 11 can slide on the surface of the female spline 21. In the present embodiment, the base layer 17 and the coating 18 are formed on the surface of the male spline 11, and no coating is formed on the surface of the female spline 21. However, the coating formation target may be the female spline 21. And you may form a film in both. In these cases, the coating may be formed after the base layer is formed on the surface of the female spline 21.

  Next, the underlayer 17 and the coating 18 will be described. The formation process of the underlayer 17 and the coating film 18 will be described with reference to FIGS. First, the surface of the base material 16 made of steel is cleaned by alkali degreasing (S1). Subsequently, a base treatment is performed to form a base layer 17 made of a phosphate such as zinc phosphate or manganese phosphate (S2). The foundation layer 17 can improve adhesion.

  Subsequently, a paint for forming the surface film 18 is applied to the surface of the base layer 17 by spraying in an air atmosphere (S3). This paint contains a mixture of an epoxy resin and a phenol resin as a binder, disulfide, polytetrafluoroethylene (PTFE) and polyethylene as a solid lubricant, and a solvent. Subsequently, firing is performed in an air atmosphere (S4). Note that although firing is performed in an air atmosphere because it is inexpensive, a nitrogen atmosphere may be used.

  The underlayer 17 and the coating 18 thus formed are as shown in FIG. That is, a base layer 17 made of phosphate having a thickness in the range of 1 to 5 μm is formed on the surface of the base material 16. The coating 18 contains a mixture 31 of an epoxy resin and a phenol resin as a binder, and disulfide 33, PTFE 34, and polyethylene 32 as solid lubricants. These component ratios are as shown in Table 1. Note that molybdenum disulfide is used as an example as a disulfide. Of course, tungsten disulfide is also applicable as the disulfide. Moreover, you may contain an additive suitably.

  The film 18 has a thickness in the range of 5 to 100 μm, and more preferably in the range of 10 to 40 μm from the viewpoint of adhesion and wear resistance. Moreover, the mass ratio of the epoxy resin as a binder and a phenol resin is 25-100 mass parts of phenol resins with respect to 100 mass parts of epoxy resins. This ratio can ensure wear resistance and toughness. Preferably, the said mass ratio is 65-75 mass parts of phenol resins with respect to 100 mass parts of epoxy resins. Here, the toughness can be increased by increasing the ratio of the epoxy resin, and the wear resistance can be improved by increasing the ratio of the phenol resin. Further, the epoxy resin may have a molecular weight of 20,000 to 30,000.

  The polyethylene 32 has an average particle diameter of 1 to 30 μm, and the mass ratio with respect to the entire coating 18 is 5 to 10 mass%. The average particle diameter of the polyethylene 32 is appropriately selected according to the film thickness of the coating 18. The disulfide 33 has an average particle size of 1 to 5 μm, and the mass ratio with respect to the entire coating 18 is 10 to 15 mass%. PTFE 34 has an average particle diameter of 1 to 10 μm, and a mass ratio with respect to the entire coating film 18 is 10 to 15 mass%. The ratio of disulfide 33, PTFE 34, and polyethylene 32 is preferably disulfide (molybdenum disulfide): PTFE: polyethylene = 3.8: 3.8: 2.5. Thus, at least the ratio of polyethylene 32 is the same as or less than that of disulfide 33 and PTFE 34.

  Here, in order to obtain the coating film 18, a paint as shown in Table 2 is preferable. Solvents include methyl ethyl ketone, toluene, xylene, propylene glycol monomethyl ether acetate, isopropyl alcohol, 1-butanol, methyl isobutyl ketone, phenol, orthocresol and the like.

Next, it is more preferable that the grease as the lubricant is based on poly α olefin (PAO). In particular, PAO having a kinematic viscosity at 40 ° C. of 1,000 to 10,000 mm ² / s or higher and a kinematic viscosity at 100 ° C. of 200 to 700 mm ² / s or higher is preferably used.

(An endurance test)
Durability tests were performed on the following Examples 1 and 2, Comparative Examples, and Reference Examples, and static friction force μs and dynamic friction force μd were measured. Here, the static friction force μs corresponds to the static friction coefficient, and the dynamic friction force μd corresponds to the dynamic friction coefficient.

(Endurance test conditions)
The durability test condition is that the second shaft member 20 is fixed and the first shaft member 10 is reciprocated in the axial direction with a twisting torque applied thereto. This is repeated until the reciprocation of the reciprocating movement reaches 6n times (n is a set value).

(Friction force measurement conditions)
The static friction force μs and the dynamic friction force μd are performed using a strain gauge attached to the female spline 21. The static friction force μs and the dynamic friction force μd are measured for the state before the start of the durability test and the number of repetitions of n, 2n, 3n, 4n, 5n, and 6n.

(Example 1 (A1))
In Example 1, a zinc phosphate coating is formed as a base layer 17 on the surface of the base material 16 of the male spline 11 formed by forging, quenching and tempering the steel S30C as the male spline 11, This is a case where the male spline 11 having the coating film 18 having the components shown in 1 is used and the grease shown in Table 3 is used as the grease as the lubricant. The film thickness of the underlayer 17 varies, and the film thickness ranges from 1 to 3 μm. The average particle diameter of polyethylene 32 in the coating 18 is 10 μm, the average particle diameter of molybdenum disulfide 33 is 3 μm, and the average particle diameter of PTFE is 5 μm. The film 18 has a thickness of 10 to 20 μm. In addition, in the grease, PTFE having an average particle diameter of 5 μm and stearic acid wax having a melting point of 220 ± 15 ° C. are used.

(Example 2 (A2))
Example 2 is a male spline in which the same base layer 17 and coating film 18 as those of Example 1 are formed on the surface of the base material 16 of the male spline 11 formed by forging, quenching, and tempering the steel S30C as the male spline 11. No. 11 is used, and the grease that is a lubricant is a mineral oil as a base oil, Li stearate (lithium soap) as a thickener, and a grease containing a molybdenum-based additive. The film thickness of the foundation layer 17 and the coating film 18 is the same as the film thickness of the foundation layer 17 and the coating film 18 of Example 1.

(Comparative Example (B))
In the comparative example, as the male spline 11, the base material 16 is exposed without forming the base layer 17 and the coating 18, and the grease of Example 2 is used as the grease as the lubricant. That is, a grease based on mineral oil is used.
(Reference example (C))
In the reference example, as the male spline 11, the same base layer 17 as that of Example 1 is formed on the surface of the base material 16 of the male spline 11 formed by forging, quenching, and tempering a steel material S30C, The male spline 11 formed with the coating film 18 having a component obtained by removing only polyethylene from the component shown in FIG. 1 and replacing the removed mass with a binder is used, and the grease of Example 1 is used as the grease as the lubricant. That is, grease using a base oil of poly α olefin is used. The film thickness of the foundation layer 17 and the coating film 18 is the same as the film thickness of the foundation layer 17 and the coating film 18 of Example 1.

(Test results)
A test result shows each of Example 1, Example 2, a comparative example, and a reference example in order of Tables 4-7. FIG. 5 shows μs / μd with respect to the number of repetitions. In FIG. 5, A1, A2, B, and C indicate Example 1, Example 2, Comparative Example, and Reference Example, respectively.

  In the comparative example (B), the static friction force μs is always larger than the dynamic friction force μd. Therefore, the vertical axis value is always larger than 1 as shown in FIG. Here, in FIG. 5, when the vertical axis value is less than 1, the μ-V characteristic has a positive slope, and when the vertical axis value is greater than 1, the μ-V characteristic has a negative slope. That is, in the comparative example (B), the μ-V characteristic is always a negative gradient. Therefore, stick slip can occur from the initial state. Furthermore, since the dynamic friction force μd decreases as the number of repetitions increases, the difference (μs−μd) between the static friction force μs and the dynamic friction force μd gradually increases. Therefore, stick slip is more likely to occur as the number of repetitions increases.

  In Example 1 (A1), it can be seen that the static friction force μs is significantly smaller than that in Comparative Example (B). Furthermore, in Example 1 (A1), the static friction force μs is smaller than the dynamic friction force μd. That is, the μ-V characteristic has a positive slope. In particular, both in the initial state and in the case where the number of repetitions increases, both the static friction force μs and the dynamic friction force μd do not change greatly, and μs / μd is substantially constant. Thus, even if the number of repetitions increases, a positive gradient μ-V characteristic can be obtained. Therefore, the occurrence of stick-slip can be reliably suppressed over a long period of time.

  In Example 2 (A2), the static friction force μs is not so different from that in Comparative Example (B). However, the dynamic friction force μd in the comparative example (B) decreases as the number of repetitions increases, whereas the dynamic friction force μd in Example 2 (A2) does not change so much even if the number of repetitions increases. Therefore, in Example 2 (A2), both the static frictional force μs and the dynamic frictional force μd are not significantly changed in both the initial state and the state where the number of repetitions is increased, and μs / μd is substantially constant. As described above, even if the number of repetitions increases, the μ-V characteristic hardly changes, and the occurrence of stick-slip can be suppressed for a long time.

  The reference example (C) has a smaller static friction force μs immediately after the start of the test than the comparative example (B). In the reference example (C), the state in which the dynamic friction force μd is larger than the static friction force μs is maintained both in the initial state and in the state where the number of repetitions is increased. That is, a positive gradient μ-V characteristic is obtained. Therefore, in Reference Example (C), the occurrence of stick slip can be suppressed over a long period of time. However, as the number of repetitions increases, both the static friction force μs and the dynamic friction force μd change.

  Example 1 (A1) is compared with Reference Example (C). In Example 1 (A1), the absolute value of the difference μs−μd between the static frictional force μs and the dynamic frictional force μd is larger than that in the reference example (C). That is, in Example 1 (A1), the static friction force μs is surely smaller than the dynamic friction force μd. Thus, according to Example 1 (A1), the positive gradient μ-V characteristic can be obtained with certainty.

  Further, in Example 1 (A1), even when the number of repetitions increases, the frictional forces μs and μd are both kept small, but in Reference Example (C), the frictional force μs increases as the number of repetitions increases. , Μd are both increased. Here, as the frictional forces μs and μd are smaller, the occurrence of stick-slip is suppressed. That is, according to Example 1 (A1), since the frictional forces μs and μd can be reduced as compared with the reference example (C), the occurrence of stick slip can be suppressed.

  From a comparison between Example 1 (A1) and Example 2 (A2) and a comparison between Example 1 (A1) and Reference Example (C), Example 1 (A1) is in an optimal state. That is, the base layer 17 and the coating film 18 are formed as in Example 2 (A2), but when grease using mineral oil as a base oil is used, or the base layer 17 and polyethylene are used as in Reference Example (C). Compared to the case of using the grease with PAO as the base oil by forming the removed film 18, the base layer 17 and the film 18 containing polyethylene are formed and the grease with the base oil as PAO is used. Become effective.

  The reason is considered as follows. The polyethylene 32 used as the solid lubricant for the coating 18 has long molecular chains entangled in the particles. The molecular structure of polyethylene 32 of the coating 18 is similar to the molecular structure of PAO used as a base oil for grease. Therefore, it is considered that PAO becomes familiar with the polyethylene 32 in the coating 18 and the PAO is infiltrated into the polyethylene 32 particles.

  In particular, by using PAO having a high kinematic viscosity as the base oil of the grease, the PAO soaked in the polyethylene 32 particles in the coating 18 forms a strong oil film, and the oil film is less likely to break. As a result, it is easy to maintain the grease holding state by the coating 18. Thereby, the said effect can be exhibited more effectively.

(Measurement of coefficient of static friction with lubricant base oil)
Next, it was measured how the static friction coefficient of the sliding member of the present invention changes depending on the type of lubricant base oil. A coating of the components shown in Table 1 was formed on a steel plate made of SPCC-SB and having a size of 35 × 70 × 0.3 mm without forming an underlayer, and used as a test piece. The film thickness varied, and the film thickness was in the range of 15-25 μm. The coating was formed by applying a coating for forming a coating on a steel plate and holding at a firing temperature of 180 ° C. for 30 minutes.

Lubricant base oil was apply | coated on the film by wiping the whole film of this test piece with the brand name Kimwipe (trademark) (made by Nippon Paper Crecia Co., Ltd.) which immersed each lubricating base oil shown later. After application, the test piece was allowed to stand for 5 minutes, and then the excess lubricant base oil on the coating was wiped off with a new brand name Kimwipe. The lubricating base oil is deposited on the test piece coating at approximately 0.03 mg / mm ² .

  The specimen is fixed to the moving table of a surface property measuring instrument (HEIDON-14DR, (registered trademark) Shinto Kagaku Co., Ltd.), and a steel ball made of JIS SUJ2 with a diameter of 10 mm is fixed to be non-rotatable. Placed on top. A weight was placed above the vertical direction of the steel ball, and the load applied to the test piece by the steel ball was 9.8N. The ball is connected to a load cell fixed to the surface property measuring machine via an arm extending in a first horizontal direction perpendicular to the vertical direction.

  Then, the moving table was reciprocated by a distance of 10 mm in the first linear direction, which is the horizontal direction, and the torque was detected by the load cell. The moving platform is accelerated in the positive direction of the first linear direction from 0 mm / min to 2,000 mm / min at a constant acceleration, and immediately decelerated to 0 mm / min at a constant acceleration equal to the constant acceleration. Immediately, in the negative direction of the first linear direction, it accelerates to -2,000mm / min with a constant acceleration, then immediately decelerates to 0mm / min with a constant acceleration equal to the constant acceleration, and slides this one time. Repeated 1,000 times.

  The static friction coefficient is the starting torque when the test piece starts to slide with respect to the steel ball when the moving table is accelerated in the positive direction of the first linear direction from 0 mm / min. Is obtained from the load applied to the test piece.

As shown in Table 8, the lubricant base oil is fluorinated oil (130mm ² / s @ 40 ° C), silicone oil (100mm ² / s @ 40 ° C), poly α olefin (30mm ² / s @ 40 ° C), ester Oil (100 mm ² / s @ 40 ° C.) and mineral oil (40 mm ² / s @ 40 ° C.) were used.

  FIG. 6 shows the measurement result of the static friction coefficient of the sliding member with respect to the number of sliding times. As shown in FIG. 6, in the case of silicone oil, it has been found that in the case of fluorine oil, the static friction coefficient is 0.2 or higher immediately after the start of measurement, and the static friction coefficient further increases when the number of sliding times exceeds 300. Is good with a coefficient of static friction of about 0.1 immediately after the start of measurement. Silicone oil has a low surface tension, so it easily penetrates into the film. However, -Si-O- bonds contained in silicone oil are fragile due to sliding, and the static friction coefficient increases rapidly when the number of sliding exceeds 500.

  In the case of mineral oil, the change in the coefficient of static friction is small, but the coefficient of static friction is a high value of about 0.18 to 0.20 immediately after the start of measurement. In the case of ester oil, the coefficient of static friction is stable at 0.13 to 0.14 immediately after the start of measurement. In the case of polyalphaolefin, it can be seen that the static friction coefficient is stable at 0.08 to 0.11 immediately after the start of measurement, which is preferable. It is considered that the above results were obtained because the poly α-olefin and the polyethylene in the film are similar in molecular structure and are easy to adjust.

(Measurement of static friction coefficient by polyethylene ratio)
Next, it was measured how the static friction coefficient of the sliding member changes when the ratio of polyethylene contained in the coating 18 is changed. Here, the grease which uses the poly alpha olefin shown in Example 1 as a base oil was used as the lubricant. The measurement conditions are the same as the measurement conditions when the type of the lubricant base oil is changed except that the coating film 18 is changed and the lubricant is used.

  Each coating 18 has a constant mass ratio of binder to solid lubricant of 2: 1, a constant mass ratio of epoxy resin to phenolic resin of 6: 4, and is composed of molybdenum disulfide and polytetrafluoroethylene (PTFE). After making the mass ratio constant at 5: 5, the mass ratio of polyethylene was changed as shown in Table 9. That is, the ratio of the mass of polyethylene to the total mass of molybdenum disulfide, PTFE and polyethylene was changed.

  In the above, the measurement result of the static friction coefficient of the sliding member with respect to the number of sliding times is shown in FIG. As shown in FIG. 7, when E1 which does not contain polyethylene in the film 18 and E2 to E3 containing polyethylene are compared, it was found that the coefficient of static friction is small by including polyethylene in the film 18. Furthermore, by including polyethylene in the coating 18, the difference in the coefficient of static friction becomes more pronounced as the number of sliding increases.

  Furthermore, when the mass ratio of molybdenum disulfide and PTFE to polyethylene (hereinafter referred to as “the mass ratio of polyethylene”) is set to 70:30, even in the initial state and when the number of sliding times increases, Smallest coefficient of static friction. In other words, when the mass ratio of polyethylene in the coating 18 is less than the above ratio, it is considered that the effect of polyethylene cannot be sufficiently exhibited. On the other hand, if the mass ratio of polyethylene in the coating 18 is larger than the above ratio, it is considered that the polyethylene absorbs grease excessively, thereby reducing the grease and consequently increasing the coefficient of static friction.

  From this result, when the mass ratio of the binder and the solid lubricant, the mass ratio of the epoxy resin and the phenol resin, and the mass ratio of molybdenum disulfide and polytetrafluoroethylene (PTFE) are constant, It can be seen that the mass ratio of polyethylene to the total mass of molybdenum disulfide, PTFE and polyethylene should be 20-40.

(Measurement of static friction coefficient by mass ratio of binder and solid lubricant)
Next, it was measured how the static friction coefficient of the sliding member changes when the mass ratio of the binder and the solid lubricant contained in the coating 18 is changed. Here, the grease which uses the poly alpha olefin shown in Example 1 as a base oil was used as the lubricant. The measurement conditions are the same as the measurement conditions when the type of the lubricant base oil is changed except that the coating film 18 is changed and the lubricant is used.

  In each coating 18, the mass ratio (P / B ratio) of the solid lubricant (P) to the binder (B) was changed to 0.6, 0.5, and 0.4. Moreover, the mass ratio of the epoxy resin and the phenol resin was constant at 6: 4, and the mass ratio of molybdenum disulfide, PTFE, and polyethylene was constant at 3.8: 3.8: 2.5.

  The measurement result of the static friction coefficient of the sliding member with respect to the number of sliding times is shown in FIG. In FIG. 8, F1, F2, and F3 indicate cases where the P / B ratios are 0.6, 0.5, and 0.4, respectively. That is, when the P / B ratio is set to 0.5, the static friction coefficient is substantially constant even when the number of sliding operations is increased. On the other hand, when the P / B ratio is 0.6 or 0.4, the static friction coefficient is changed when the number of sliding is increased. Thus, when the P / B ratio is 0.5, the static friction coefficient is stable over a long period of time. That is, it can be seen that the P / B ratio should be 0.43 to 0.58.

(Measurement of friction coefficient with respect to sliding speed)
Next, when the type of coating 18 and the type of lubricant were as follows, a ring-on-block test was performed to measure the coefficient of friction. For the test body F1, as shown in Example 1, as a coating of S30C, a coating containing a solid lubricant containing polyethylene was formed on a resin binder, and grease using PAO as a base oil was used as the lubricant. The test body F2 does not form a film, but uses a grease containing mineral oil as a base oil and containing a molybdenum-based additive. The specimen F3 uses a grease that forms diamond-like carbon (DLC) as a coating of S30C, uses mineral oil as a base oil, and does not contain a molybdenum-based additive.

  In the ring-on-block test, each of the above specimens was used as a block, a load of 50 N was applied to the ring using S30C, and the sliding speed was 0.009 m / s, 0.018 m / s, 0.037 m / s, 0.073 m / The coefficient of friction was measured in a state where the velocity was changed to s, 0.147 m / s, 0.073 m / s, 0.037 m / s, 0.018 m / s, and 0.009 m / s and held at each speed for a certain period of time.

  The measurement result of the test body F1 is shown in FIG. 9, the measurement result of the test body F2 is shown in FIG. 10, and the measurement result of the test body F3 is shown in FIG. FIGS. 9 to 11 each show a case where the sliding speed is increased and a case where the sliding speed is decreased.

  From FIG. 9, the test body F1 corresponding to Example 1 has a larger friction coefficient as the sliding speed increases, and the friction coefficient becomes smaller as the sliding speed decreases. That is, it can be seen that the μ-V characteristic is a positive gradient. On the other hand, the specimens F2 and F3 have a smaller coefficient of friction as the sliding speed increases and a larger coefficient of friction as the sliding speed decreases. That is, it can be seen that the μ-V characteristic has a negative slope. In particular, it can be seen that the specimen F1 has a smaller coefficient of friction when the sliding speed is smaller than the other specimens F2 and F3.

10: First shaft member, 11: Male spline, 16: Base material, 17: Underlayer, 18: Coating, 20: Second shaft member, 21: Female spline, 31: Binder, 32: Polyethylene, 33: Disulfide object

Claims (5)

A sliding member having a coating on the surface and sliding in the presence of a lubricant,
The coating is
As binder, epoxy resin and phenol resin,
As a solid lubricant, at least one disulfide of molybdenum disulfide and tungsten disulfide, polytetrafluoroethylene (PTFE), and polyethylene,
A sliding member. The mass ratio of the epoxy resin and the phenol resin is 25 to 100 parts by mass of the phenol resin with respect to 100 parts by mass of the epoxy resin,
The sliding member according to claim 1, wherein a mass ratio of the polyethylene to the entire coating film is 5 to 10 mass%.   The sliding member according to claim 1, wherein the lubricant contains polyα-olefin (PAO) as a base oil. The sliding member according to claim 3, wherein the base oil has a 40 ° C. kinematic viscosity of 1,000 mm ² / s or more.   The sliding member according to any one of claims 1 to 4, wherein the sliding member is a spline shaft that slides in an axial direction.

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