JP4461871B2 - SEALING DEVICE AND BEARING DEVICE PROVIDED WITH THE SEALING DEVICE - Google Patents

Description

  The present invention relates to a sealing device and a bearing device including the sealing device.

  In the bearing device, oil is applied to the sliding surface in order to reduce the friction between the sliding portion of the sealing device of the bearing device and the sliding surface of the bearing ring on which the sliding portion slides. Yes.

  However, since the oil present between the sliding surface and the sliding portion is easy to move, the bearing device is likely to be in a dry state where no oil exists between the sliding surface and the sliding portion. Then, there is a problem that a stick-slip phenomenon frequently occurs between the sliding surface and the sliding portion, particularly in a region where the rotational speed is small. For this reason, there is a problem in that the sliding part is heavily worn and squealing is frequently generated.

In order to avoid the above problem, that is, to reduce the wear of the sliding part and the squealing noise, if the friction between the sliding part and the sliding surface is set to a small value, the sliding part and the sliding part There is a problem that oil leaks from between the moving surfaces.
JP 2003-166549 A

  SUMMARY OF THE INVENTION An object of the present invention is to provide a seal device that can prevent the sliding portion from being worn out and hardly generate squealing noise, and that can reliably prevent oil leakage, and a bearing device including the seal device.

  In order to solve the above problems, a sealing device of the present invention includes an elastic member having a sliding portion, and the ten-point average roughness Rz of the sliding portion is 10 μm <Rz <100 μm. The average interval Sm of the irregularities is Sm <40 μm, and the amplitude distribution curve (probability density function) ADF of the sliding portion is characterized by having only one peak.

Here, the ten-point average roughness (Rz) is the interval between the average of the top of the roughness surface from the highest to the fifth and the average of the bottom from the deepest to the fifth in the two-dimensional case.
Rz = (1/5) ((P1 + P2 + P3 + P4 + P5) − (V1 + V2 + V3 + V4 + V5)) (FIG. 8 shows P1 to P3 and V1 to V3 in a one-dimensional (curved) example)
(ISO standard 4287/1).

Further, in the case of two dimensions, the average interval (Sm) of the unevenness is that only one line is extracted from the roughness curved surface in the X direction, and the point from the peak to the valley is the change point, and from the change point to the next change point. Obtain the average value of the intervals. This is repeated for the Y direction of the measurement range, and the average of the values obtained for all lines is obtained (Smx). Similarly, only one line is extracted in the Y direction, the point from the peak to the valley is taken as the change point, and the average value of the interval from the change point to the next change point is obtained. This is repeated for the X direction of the measurement range, and the average of the values obtained for all lines is obtained (Smy).
Smx = (S1 + S2 +... + Sn) / n,
Smy = (S1 + S2 +... + Sn) / n,
And it defines as Sm calculated as follows from this Smx and Smy.
Sm = (Smx ² + Smy ² ) ^1/2 (FIG. 9 shows S1 to S4 in a one-dimensional (curved) example)
(ISO standard 4287/1).

In addition, the amplitude distribution curve (probability density function) (ADF) is, in one dimension, the length of the roughness curve existing in the roughness curved surface when it is cut at a constant width (1%). It is a graph of the percentage with respect to the measurement length, and as in the present invention, in two dimensions, the roughness curve is expanded to a roughness curved surface. (FIG. 10 shows a one-dimensional (curved) example)
(ISO standard 4287/1).

  According to the sealing device of the present invention, the ten-point average roughness Rz of the sliding portion is set to a value larger than 10 μm, and the size of the unevenness formed on the sliding portion is set to a certain level or more. Therefore, an oil sump for accumulating oil can be formed in the concave and convex valley portions formed in the sliding portion, and the sliding portion and the sliding surface on which the sliding portion slides can be formed. The oil can be reliably held, and the state between the sliding portion and the sliding surface can be prevented from becoming a dry state in which there is no oil and a squeak noise is easily generated. Moreover, the flexibility of the sliding part can be increased, and the friction between the sliding part and the sliding surface can be reduced. Therefore, it is possible to suppress the generation of squeal between the sliding portion and the sliding surface, and it is possible to suppress the wear of the sliding portion, thereby extending the life of the sealing device. Further, the torque can be reduced and the operating cost can be reduced. If the ten-point average roughness Rz of the sliding portion is set to be less than 10 μm, there arises a problem that a squeal is generated.

  Further, according to the sealing device of the present invention, the Rz of the sliding part is set to a value smaller than 100 μm, and the size of the unevenness formed on the sliding part is set to a certain level or less. It is possible to prevent oil leakage from occurring between the sliding portion and the sliding surface on which the sliding portion slides without the unevenness formed on the moving portion becoming excessively large. On the other hand, when Rz of the sliding part is set to 100 μm or more, there arises a problem that oil leakage occurs.

  Further, according to the sealing device of the present invention, the sliding portion has an average interval Sm smaller than 40 μm, and the interval between the crest of the sliding portion and the next crest is smaller than a predetermined interval. Since the flatness of the moving part is smaller than the predetermined flatness, the amount of oil that can be accommodated in the concave and convex valleys of the sliding part can be made a certain amount or more, and the flexibility of the sliding part is also improved. Can be more than a certain amount. Therefore, it is possible to further suppress the generation of squeaking noise generated between the sliding portion and the sliding surface on which the sliding portion slides and the wear of the sliding portion. If the average interval Sm of the sliding parts is set to 40 μm or more, there arises a problem that a squeal is generated.

  Further, according to the sealing device of the present invention, the amplitude distribution curve (probability density function) of the sliding portion has only one peak, that is, the deepest valley height in the sliding portion. , With the highest number of mountains located in an area of a certain height, lower than the area with the highest number of mountains, and the area with the highest number of mountains. In the region where the height is high, the number of peaks decreases as the distance from the region where the number of peaks is the largest, so that the oil retaining effect of the sliding portion can be increased. Therefore, the generation of squealing can be further suppressed. If the amplitude distribution curve (probability density function) of the sliding portion is set so as to have two or more peaks, there is a problem that a squeal is generated.

  Moreover, the sealing device of one embodiment is characterized in that the amplitude distribution curve of the sliding portion follows a substantially normal distribution.

According to the sealing device of the above embodiment, the amplitude distribution curve of the sliding portion has a substantially normal distribution, that is, the amplitude distribution curve of the sliding portion has one peak and the peak Since the curve is symmetrical, the number of peaks located at the midpoint between the height of this valley and the height of the highest mountain when the height of the deepest valley is taken as a reference in the sliding part. , Almost the most. Therefore, the oil retaining effect of the sliding portion can be further increased, and the generation of squealing can be further suppressed.
Moreover, the sealing device of one embodiment is as follows.
The elastic member is any one of nitrile rubber, acrylic rubber, and fluorine rubber.
Moreover, the sealing device of one embodiment is as follows.
The sliding surface on which the sliding portion slides is characterized in that the material is steel.

  The bearing device of the present invention is characterized by including the seal device of the present invention.

  According to the bearing device of the invention, since the seal device of the invention is provided, torque can be reduced, generation of squealing noise can be prevented, and oil leakage can be reliably prevented.

  According to the sealing device of the present invention, the ten-point average roughness Rz of the sliding portion is set to a value larger than 10 μm, so that oil is stored in the uneven valley portion formed in the sliding portion. An oil sump can be formed, and the flexibility of the sliding portion can be increased. Therefore, the generation of squeaking between the sliding portion and the sliding surface can be suppressed, the wear of the sliding portion can be suppressed, the life of the sealing device can be extended, and the torque can be reduced. Operating costs can be reduced.

  Further, according to the sealing device of the present invention, since the Rz of the sliding portion is set to a value smaller than 100 μm, the unevenness formed on the sliding portion does not become too large, and the sliding portion and Oil leakage can be prevented from occurring between the sliding surface on which the sliding portion slides.

  Further, according to the sealing device of the present invention, since the Sm of the sliding portion is made smaller than 40 μm and the flatness of the sliding portion is made smaller than a certain degree, The amount of oil that can be accommodated can be made a certain amount or more, and the flexibility of the sliding portion can also be made a certain amount or more. Therefore, it is possible to further suppress the generation of squeal generated between the sliding portion and the sliding surface and the wear of the sliding portion.

  Further, according to the sealing device of the present invention, the amplitude distribution curve (probability density function) of the sliding portion has only one peak, so that the oil retaining effect of the sliding portion is increased. Can be further suppressed.

  Hereinafter, the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a cross-sectional view of a sealing device according to an embodiment of the present invention.

  This sealing device is a sealing device that seals between an inner ring and an outer ring of a bearing device (not shown), and a cored bar member 1 and an elastic member fixed to the cored bar member 1 so as to substantially surround the cored bar member 1. It consists of two. The elastic member 2 is formed using nitrile rubber (NBR) which is the most common material in the oil seal of the bearing device. The upper side (outer side in the radial direction of the bearing device) of the sealing device is a fixing portion 3 that is fixed to the outer ring (not shown). The lower side of the sealing device is the left side of the paper ( The seal lip 4 protrudes inward in the axial direction of the bearing device.

  The surface on the left side of the paper surface of the seal lip portion 4 is a sliding portion 5 that slides on the outer peripheral surface of the inner ring (not shown) during operation of the bearing device. The sliding portion 5 is formed with unevenness by transferring the unevenness of the mold surface during vulcanization molding.

  The ten-point average roughness Rz of the sliding part 5 is set to 10 μm <Rz <100 μm, and the average interval Sm of the sliding part 5 is set to Sm <40 μm. The sliding portion 5 is designed so that the amplitude distribution curve has one peak.

  FIG. 2 is a cross-sectional view of a testing machine for measuring the presence or absence of a squeal of the sealing device, measuring friction torque, and observing oil leakage.

  In the following, an explanation of the structure of this testing machine, a method for determining the presence or absence of squealing, a method for measuring friction torque, and a method for observing oil leakage will be described with reference to FIG.

  In FIG. 2, 21 is a housing of the testing machine, 22 is an oil tank of the testing machine, and 23 is a rotating shaft of the testing machine. Further, 24 is an outer ring, 25 is an inner ring made of ordinary hardened bearing steel (SUJ2), and 26 is an elastic member made of nitrile rubber.

  As shown in FIG. 2, the housing 21 is formed in a cylindrical shape. The oil tank 22 is fixed to one end of the housing 21 so that oil can be accommodated in the internal space thereof. An oil injection hole 28 for injecting oil is formed in the upper part of the oil tank 22 in the vertical direction. The outer ring 24 is formed in a cylindrical shape, and the elastic member 26 is formed in a disk shape in which a cylindrical through hole is formed at the center. The inner ring 25 is formed in a disc shape, and the diameter thereof is larger than the diameter of the through hole. Moreover, the said rotating shaft 23 is a cylindrical-shaped rod member, The diameter is smaller than the diameter of the said through-hole. The rotating shaft 23 can move in the axial direction of the housing about the center of the cylindrical inner region of the housing 21.

  Using the testing machine, the outer ring 24, the inner ring 25, and the elastic member 26, generation of squeal and measurement of friction torque are performed as follows.

  First, various surface unevenness treatments are performed on the sliding portion around the through hole on one end surface of the elastic member 26, and then the roughness of the sliding portion subjected to the surface unevenness treatment is observed with a laser microscope. . Then, from this observation result, the Rz and Sm of the sliding portion of the elastic member 26 and the peak number of the amplitude distribution curve are calculated.

  Next, as shown in FIG. 2, the cylindrical outer peripheral surface of the elastic member 26 is fixed to one end of the cylindrical inner peripheral surface of the outer ring 24, and the cylindrical outer peripheral surface of the outer ring 24 is further tested. It fixes to the cylindrical internal peripheral surface of the housing 21 of a machine. Further, the rotational shaft 23 is disposed so as to penetrate the substantially central portion of the through hole, and after fixing the substantially central portion of one end surface of the inner ring 25 to the end surface on one side of the rotational shaft, The rotation shaft 23 is moved in the axial direction, and the rotation shaft 23 is arranged at a predetermined position. In this way, the peripheral portion of one end surface of the disk-shaped inner ring 25 is pressed against the sliding portion formed by the peripheral portion of the through hole on the one end surface of the elastic member 26, and the periphery of the one end surface of the inner ring 25 is The part is brought into contact with the sliding part with a tightening margin of 0.2 mm.

Finally, in a state where the oil tank 22 is not filled with the oil tank 22 and the oil tank 22 is empty, the rotation shaft 23 is rotated at 0 to 1500 min ⁻¹ (sliding speed 0.0 to 1.5 m / s). Rotate with a number to measure the friction torque and check for noise by hearing.

  Further, oil leakage is observed as follows using the test machine, the outer ring 24, the inner ring 25, and the elastic member 26.

  First, various surface unevenness treatments are performed on the sliding portion around the through hole on one end surface of the elastic member 26, and then the roughness of the sliding portion subjected to the surface unevenness treatment is observed with a laser microscope. . Then, from this observation result, the Rz and Sm of the sliding portion of the elastic member 26 and the peak number of the amplitude distribution curve are calculated.

  Next, as shown in FIG. 2, the cylindrical outer peripheral surface of the elastic member 26 is fixed to one end of the cylindrical inner peripheral surface of the outer ring 24, and the cylindrical outer peripheral surface of the outer ring 24 is further tested. It fixes to the cylindrical internal peripheral surface of the housing 21 of a machine. Further, the rotational shaft 23 is disposed so as to penetrate the substantially central portion of the through hole, and after fixing the substantially central portion of one end surface of the inner ring 25 to the end surface on one side of the rotational shaft, The rotation shaft 23 is moved in the axial direction, and the rotation shaft 23 is arranged at a predetermined position. In this way, the peripheral portion of one end surface of the disk-shaped inner ring 25 is pressed against the sliding portion formed by the peripheral portion of the through hole on the one end surface of the elastic member 26, and the periphery of the one end surface of the inner ring 25 is The part is brought into contact with the sliding part with a tightening margin of 0.2 mm.

  Finally, silicone oil having a viscosity of 20 cts is injected from the oil injection hole 28 of the oil tank 22, the oil tank 22 is filled with oil, and after waiting for 30 minutes, the presence or absence of oil leakage is visually determined.

  FIG. 3 is a diagram showing the relationship between the number of peaks of Rz, Sm, and the amplitude distribution function, the presence / absence of squealing, and the presence / absence of oil leakage.

  In FIG. 3, Sm on the vertical axis represents the average distance between the sliding portions of the elastic member 26 used in the measurement, and Rz on the horizontal axis represents the ten-point average of the sliding portions of the elastic member 26 used in the measurement. Roughness is shown.

  In FIG. 3, ♦ indicates a sample (elastic member 26) in which the amplitude distribution function of the sliding portion of the elastic member 26 used in the above measurement has one peak and no squeal is generated, and ■ indicates , Shows a sample in which the amplitude distribution function of the sliding portion of the elastic member 26 used in the measurement has one peak and a squeak is generated, and ▲ indicates the amplitude of the sliding portion of the elastic member 26 used in the measurement. Samples with two distribution function peaks and squealing are shown, and ● shows samples with oil leakage.

  As shown in FIG. 3, in the sample (elastic member 26) having Rz of 100 μm or more, oil leakage occurs without exception. When Rz is set to 100 μm or more, the elastic member does not perform the sealing function.

  Further, a sample (elastic member 26) having an Rz of 10 μm or less generates squealing noise without exception, and if the Rz is set to 10 μm or less, the elastic member becomes unqualified as a seal mechanism.

  In addition, in a sample (elastic member 26) having Sm of 40 μm or more, a squeal is generated without exception even if the peak of the amplitude distribution function of the sliding portion of the elastic member is one or two, and Sm is 40 μm. If it sets to the above, an elastic member will become unqualified as a seal mechanism.

  On the other hand, when Rz is 10 μm <Rz <100 μm and Sm is limited to the range of Sm <40 μm, a sample that generates squeal noise with one peak and a sample that leaks oil are included in this region. In this region, there are only a sample with one peak and no squeal and a sample with two peaks and squeal. Therefore, if the condition of one peak is further applied in this region, the sample that satisfies this condition does not leak oil and does not generate a squeal.

  From this, if the seal device is made using one sliding portion where Rz is 10 μm <Rz <100 μm, Sm is Sm <40 μm, and the number of peaks of the amplitude distribution function is one. An ideal sealing device that does not cause oil leakage and does not generate squealing noise can be configured.

  4, 5, 6 and 7 are diagrams showing the relationship between the shape of the amplitude distribution function and the presence or absence of generation of friction torque and squealing noise with respect to the rotational speed.

  Specifically, FIGS. 4A, 5A, 6A, and 7A show amplitude distribution functions (probability density functions). 4A, FIG. 5A, FIG. 6A, and FIG. 7A, the horizontal axis indicates the cutting level C, and the vertical axis indicates the probability density. 4B, FIG. 5B, FIG. 6B, and FIG. 7B show the amplitude distribution functions in FIG. 4A, FIG. 5A, FIG. 6A, and FIG. FIG. 8 is a diagram showing the friction torque of the rotating shaft 23 caused by the friction between the inner ring 25 and the elastic member 26 with respect to the rotational speed of the rotating shaft 23 in the case of FIG.

  4B, FIG. 5B, FIG. 6B, and FIG. 7B, ◆ indicates a sample (elastic member 26) that did not generate squeal, and ■ indicates squeal. A sample (elastic member 26) in which sound is generated is shown.

  Further, the sample used for the measurement shown in FIG. 4 has an Rz of 33.23 μm and an Sm of 38.18 μm, and the sample used for the measurement shown in FIG. 5 has an Rz of 4.01 μm. , Sm is 41.85 μm. Further, the sample used for the measurement shown in FIG. 6 has an Rz of 108.16 μm and Sm of 8.72 μm, and the sample used for the measurement shown in FIG. 7 has an Rz of 31.48 μm. , Sm is 24.10 μm.

  In addition, the samples used in the measurements shown in FIGS. 4, 5, and 7 are confirmed to have no oil leak in the observation of the oil leak, while the samples used in the measurement shown in FIG. It has been confirmed that oil leakage occurs in observation of oil leakage.

  As shown in FIG. 4A, Rz is 33.23 μm, Sm is 38.18 μm, and the values of Rz and Sm are appropriate as in the sample used in the measurement shown in FIG. In addition, when there are two peaks in the amplitude distribution function, as shown in FIG. 4B, a squeaking noise is frequently generated in a region where the rotational speed of the rotating shaft is small. For this reason, the sample having two peaks frequently causes a stick-slip phenomenon in a region where the rotational speed of the rotating shaft is small, and is not suitable as a seal mechanism.

  Further, as shown in FIG. 5A, even when the amplitude distribution function has only one peak, Rz is 4.01 μm, which is below the appropriate range larger than 10 μm, and Sm is , 41.85 μm, which exceeds the appropriate range smaller than 40 μm, as shown in FIG. 5 (B), squeaking noise is frequently generated in a region where the rotational speed of the rotating shaft is small. For this reason, when Rz is below the proper range and Sm is above the proper range, a stick-slip phenomenon frequently occurs in a region where the rotational speed of the rotary shaft is small, which is not suitable as a seal mechanism.

  Further, as shown in FIG. 6A, even if the amplitude distribution function has only one peak and Sm is 8.72 μm, which is smaller than 40 μm and within an appropriate range, Rz If the value exceeds 108.16 μm, which is an appropriate range smaller than 100 μm, oil leakage occurs and the sealing function is not performed.

  On the other hand, as shown in FIG. 7A, the amplitude distribution function has only one peak, both side portions of the peak in the amplitude distribution function are substantially symmetrical with respect to the peak, and the amplitude distribution function is substantially As shown in FIG. 7B, when the normal distribution is followed, Rz is 31.48 μm, Sm is 24.10 μm, and both Rz and Sm are set to appropriate values, as shown in FIG. No squeal is generated regardless of the value of the number. Further, the value of the friction torque is very small as compared with the samples of FIGS. 4 and 5 which are other samples that do not cause oil leakage, regardless of the rotational speed. When the sealing device is formed, the operating cost of the sealing device can be greatly reduced.

  According to the sealing device of the above embodiment, the ten-point average roughness Rz of the sliding portion 5 is set to a value larger than 10 μm, and the size of the unevenness formed on the sliding portion 5 is larger than a certain level. Therefore, an oil sump for accumulating oil can be formed in the concave and convex valley portions formed in the sliding portion 5, and the sliding portion 5 and the sliding surface on which the sliding portion 5 slides Oil (not shown) can be securely held, and the state between the sliding portion 5 and the sliding surface is prevented from becoming a dry state in which there is no oil and a squealing noise is likely to occur. it can. Moreover, the flexibility of the sliding part 5 can be increased, and the friction between the sliding part 5 and the sliding surface can be reduced. Therefore, the generation of squeaking between the sliding portion 5 and the sliding surface can be suppressed, and the wear of the sliding portion 5 can be suppressed, so that the life of the sealing device can be extended.

  Further, according to the sealing device of the above-described embodiment, the Rz of the sliding portion 5 is set to a value smaller than 100 μm, and the size of the unevenness formed on the sliding portion 5 is set to a certain size or less. Therefore, the unevenness | corrugation formed in the sliding part 5 does not become large too much, and it can prevent that oil leaks from between the sliding part 5 and the said sliding surface.

  Further, according to the sealing device of the above embodiment, the average interval Sm of the sliding portion 5 is made smaller than 40 μm, and the interval between the peak and the next peak in the slide 5 is made smaller than a predetermined interval. Since the flatness of the sliding portion 5 is made smaller than the predetermined flatness, the amount of oil that can be accommodated in the concave and convex valley portions of the sliding portion 5 can be made a certain amount or more. The amount of flexibility can also be a certain amount or more. Therefore, it is possible to further suppress the generation of squeaking noise generated between the sliding portion 5 and the sliding surface and the wear of the sliding portion 5.

  Further, according to the sealing device of the above embodiment, the amplitude distribution curve (probability density function) of the sliding portion 5 has only one peak, that is, the deepest valley in the sliding portion 5. When the height of the mountain is used as a reference, the number of mountains located in a certain height area is the largest, and the area that is lower than the area with the largest number of mountains and the largest number of mountains. In the region where the height is higher than the region, the number of peaks decreases as the distance from the region having the largest number of peaks increases, so that the oil retaining effect of the sliding portion 5 can be increased. Therefore, the generation of squealing can be further suppressed.

  In the present invention, the amplitude distribution curve of the sliding portion is a curve that follows a substantially normal distribution, that is, the amplitude distribution curve of the sliding portion has a single peak and is a symmetrical curve with respect to this peak. In some cases, as shown in FIG. 7, an ideal sealing device that does not generate squeal, does not cause oil leakage, and has a very low friction torque and a very low operating cost regardless of the rotational speed. Can be built.

  Further, when the seal device of the present invention is employed as the seal device of the bearing device, it is possible to configure a bearing device that can reduce torque, generate no squeal, and reliably prevent oil leakage.

  In the sealing device of the above embodiment, nitrile rubber (NBR) is adopted as the material of the elastic member 5, but in the sealing device of the present invention, nitrile rubber (NBR) such as acrylic rubber or fluorine rubber is used as the material of the elastic member. A rubber material other than the above may be used, and in this case, as in the case where nitrile rubber (NBR) is used as the material of the elastic member 5, the torque can be reduced and the generation of squealing can be suppressed, and , Oil leakage can be surely prevented.

  Further, in the above measurement, ordinary hardened bearing steel (SUJ2) is adopted as the material of the inner ring. In this case, the torque can be reduced and no squeal is generated, as in the case of adopting the normally hardened bearing steel (SUJ2) as the material of the inner ring. Oil leakage can be reliably prevented.

  In the above measurement, a silicone oil having a viscosity of 20 cts was adopted. However, in the sealing device of the present invention, any oil other than a silicone oil having a viscosity of 20 cts can be used as long as the oil is used for a bearing device. However, oil leakage can be reliably prevented.

It is sectional drawing of the sealing device of one Embodiment of this invention. It is sectional drawing of the testing machine for performing the presence or absence of the noise of a sealing apparatus, the measurement of a friction torque, and observation of an oil leak. It is a figure which shows the relationship between the number of peaks of Rz, Sm, and an amplitude distribution function, the presence or absence of squealing, and the presence or absence of oil leakage. It is a figure which shows the relationship between the shape of an amplitude distribution function, and the friction torque with respect to rotation speed. It is a figure which shows the relationship between the shape of an amplitude distribution function, and the friction torque with respect to rotation speed. It is a figure which shows the relationship between the shape of an amplitude distribution function, and the friction torque with respect to rotation speed. It is a figure which shows the relationship between the shape of an amplitude distribution function, and the friction torque with respect to rotation speed. It is a figure explaining the one-dimensional ten-point average roughness. It is a figure explaining a one-dimensional average space | interval. It is a figure explaining a one-dimensional amplitude distribution curve.

DESCRIPTION OF SYMBOLS 1 Core metal member 2,26 Elastic member 5 Sliding part

Claims (5)

An elastic member having a sliding portion;
The ten-point average roughness Rz of the sliding part is
10 μm <Rz <100 μm,
The average interval Sm of the unevenness of the sliding portion is:
Sm <40 μm,
The amplitude distribution curve of the sliding portion has only one peak. The sealing device according to claim 1,
An amplitude distribution curve of the sliding portion follows a substantially normal distribution. The sealing device according to claim 1 or 2,
The sealing device according to claim 1, wherein the elastic member is any one of nitrile rubber, acrylic rubber, and fluorine rubber. The sealing device according to any one of claims 1 to 3,
The sliding device on which the sliding portion slides is made of steel. A bearing device comprising the seal device according to any one of claims 1 to 4.

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