JP2009138801A - Thrust washer and crankshaft support structure - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a thrust washer and a crankshaft support structure having enhanced durability and restraining friction and abrasion by local loading by enhancing absorptivity to deformation of a shaft or a bearing after installation. <P>SOLUTION: The thrust washers 20 and 22 are formed by sandwiching a rubber material 28 between metallic plates 24 and 26. Thus, even if local pressure in the axial direction is generated when a deformation part 4b is generated on the journal bearing 4 side, the thrust washers 20 and 22 generate and absorb compressive deformation in the local thickness direction. Thus, since the pressure is widely dispersively transmitted to the opposed surface 10b side of a crankshaft 10, a local pressure increase to the crankshaft 10 side can be restrained. Since the sliding surface side is formed of a metallic material of any of the metallic plates 24 and 26, durability becomes high, and separation and a crack are hardly caused. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a thrust washer disposed between axially opposed surfaces of a shaft and a bearing, and a crankshaft support structure using the thrust washer.

  A thrust washer is known that is disposed between axially opposed surfaces of a shaft and a bearing. For example, a metallic thrust disposed between a crankshaft of an internal combustion engine and a journal bearing or bearing cap (including a bearing cap connection structure such as a bearing beam and a ladder beam) that supports the crankshaft at the lower portion of the cylinder block Washers are known.

As such a thrust washer, one formed mainly of a resin instead of a metal material is known (see, for example, Patent Documents 1 and 2). Further, Patent Document 2 proposes a composite with a metal.
JP 5-78500 A (page 2-3) JP-A-5-296234 (pages 7-9)

  Metal thrust washers have poor absorbency against deformation of the shaft or bearing after assembly and tend to increase friction and wear due to local contact, resulting in problems with durability and energy consumption.

  Since the materials shown in Patent Documents 1 and 2 are all or mainly composed of resin, they have sufficient absorbability against deformation of the shaft or bearing, but at least the sliding surface is resin and is more durable than metal. It is poor in properties, and peeling or cracking occurs depending on the use site. In particular, when a crankshaft of an internal combustion engine is supported, there is a possibility that a local contact becomes stronger due to a difference in thermal expansion between the crankshaft and the cylinder block side, resulting in a problem of durability.

  It is an object of the present invention to increase the absorbability of the assembled shaft or bearing after deformation to suppress friction and wear due to local contact and to enhance durability.

In the following, means for achieving the above object and its effects are described.
The thrust washer according to claim 1 is a thrust washer disposed between the axially opposed surfaces of the shaft and the bearing, wherein the sliding surface side of one of the opposed surfaces is a metal material, It is characterized in that a compression deformation portion is formed which causes a local compressive deformation in the thickness direction in response to a local axial pressure from the other side.

  As described above, the thrust washer according to the present invention forms the above-described compression deformed portion, so that even if local axial pressure is generated from the opposing surface, the thickness in the local thickness direction corresponding to this pressure is generated. It will be compressed and deformed. As a result, the pressure is transmitted in a widely dispersed manner on the other facing surface side, so that a local pressure increase on the sliding surface can be suppressed. Thus, the absorbency with respect to the deformation | transformation of the axis | shaft or bearing after an assembly | attachment can be improved, and the friction and abrasion by a local part can be suppressed.

Moreover, since the sliding surface side is made of a metal material, the durability is high, and peeling and cracking are unlikely to occur.
The thrust washer according to claim 2 is characterized in that, in claim 1, the compression deformation portion is formed of a metal composite in which a resin elastic body is disposed between two metal plates. To do.

  By forming the compression deformation portion on the thrust washer in this way, even if axial pressure is generated on the opposed surface with which the thrust washer abuts, it is absorbed by local compression deformation in the thickness direction corresponding thereto. . Thus, as described above, the local pressure increase on the sliding surface can be suppressed, the absorbability against the deformation of the shaft or the bearing after assembly is increased, and the friction and wear due to local contact can be suppressed.

Moreover, both sides of the compression deformed portion are metal plates, and even if any of them is a sliding surface, the durability is high, and peeling and cracking are unlikely to occur.
The thrust washer according to claim 3 is characterized in that, in claim 2, one or both of the two metal plates are spring steel plates and are formed in a corrugated plate shape.

  Thus, by forming the metal plate in the shape of a corrugated plate with a spring steel plate, it is possible to further increase the absorbability against deformation of the shaft or the bearing after assembly, and effectively suppress friction and wear due to local contact. be able to.

  The thrust washer according to claim 4 is the thrust washer according to claim 1, wherein the entire thrust washer is made of a single spring steel plate, and a part or all of the spring steel plate is formed in a corrugated shape, whereby the compression deformation portion is formed. It is formed.

  Thus, the thrust washer which consists of one spring steel plate forms the compression deformation part by making a part or all of the spring steel plate into the corrugated plate shape. As a result, even if a local axial pressure is generated from the opposing surface, a local compressive deformation in the thickness direction of the spring steel plate itself can be generated and absorbed accordingly. Thus, as described above, the local pressure increase on the sliding surface can be suppressed, the absorbability against the deformation of the shaft or the bearing after assembly is increased, and the friction and wear due to local contact can be suppressed.

Moreover, since the entire thrust washer is a single spring steel plate, the durability is high and peeling and cracking are unlikely to occur.
The thrust washer according to claim 5 is a thrust washer disposed between the axially facing surfaces of the shaft and the bearing, and is provided on a surface of the metal support plate on the side receiving the pressure in the local axial direction. A paper lining layer is provided.

  By providing a paper lining layer in this way, the flexibility of the paper lining increases the absorbability against deformation of the shaft or bearing after assembly, suppresses friction and wear due to local contact, and makes it difficult to cause peeling and cracking. . And since paper lining is supported by the metal support plate, durability can be improved as a whole.

  A thrust washer according to claim 6 is characterized in that, in claim 5, a paper lining layer is thinned or not provided in a region of the surface that receives local axial pressure.

  In particular, the paper lining in the area that receives the local axial pressure is thin or not provided, so that even if a deformation that transmits the local axial pressure from the opposite surface occurs, this deformation is absorbed. Can do. From this, the local pressure rise of the sliding surface can be more effectively suppressed. Thus, the high absorbency with respect to the deformation | transformation of the axis | shaft or bearing after an assembly | attachment is produced, and the friction and wear by a local part can be suppressed effectively.

  A thrust washer according to a seventh aspect is characterized in that, in any one of the first to sixth aspects, the shaft is a crankshaft of an internal combustion engine, and the bearing is a journal bearing or a bearing cap of a cylinder block.

  As described above, the thrust washer described above can be applied as a thrust washer disposed between opposed surfaces in the axial direction, with a shaft serving as a crankshaft and a bearing serving as a journal bearing or bearing cap of a cylinder block. As a result, in the bearing portion of the crankshaft of the internal combustion engine, it is possible to increase the absorbability against deformation of the journal bearing or bearing cap of the cylinder block after assembly, thereby suppressing friction and wear due to local contact and improving durability. .

A thrust washer according to an eighth aspect is characterized in that, in any one of the first to seventh aspects, a solid lubricating film is formed on a sliding surface with respect to one of the opposing surfaces.
Thus, by forming a solid lubricating film on the sliding surface, friction and wear can be further suppressed, and durability can be further enhanced.

  In the crankshaft support structure according to the ninth aspect, no thrust washer is provided between the axially opposed surfaces of the crankshaft and the bearing cap of the internal combustion engine, and the axial shaft between the crankshaft and the journal bearing of the cylinder block is provided. The thrust washer according to any one of claims 1 to 8 is arranged between the opposing surfaces.

  In this way, when the thrust washer is not provided between the axial facing surfaces of the crankshaft and the bearing cap, if the bearing cap is bolted to the journal bearing side of the cylinder block, the journal bearing of the cylinder block will be deformed. After installation, the thrust washer creates a risk of local contact. However, as described above, the thrust washer used in this crankshaft support structure has improved absorbability against deformation of the shaft or bearing after assembly, so it can suppress friction and wear due to local contact and has high durability. , Peeling and cracking are less likely to occur.

  The crankshaft support structure according to claim 10, wherein a thrust washer is provided between the axial facing surfaces of the crankshaft of the internal combustion engine and the journal bearing of the cylinder block, and the axial facing surfaces of the crankshaft and the bearing cap are provided. The thrust washer according to any one of claims 1 to 8 is arranged between them.

  In the case of a type in which a thrust washer is provided between the axially opposed surfaces of the crankshaft and the bearing cap, the thrust washer generates vibration in the axial direction of the crankshaft at the radial end of the bearing cap during operation of the internal combustion engine. Due to this vibration deformation, the thrust washer has a risk of local contact. However, as described above, the thrust washer used in this crankshaft support structure has improved absorbability against deformation of the shaft or bearing after assembly, so it can suppress friction and wear due to local contact and has high durability. , Peeling and cracking are less likely to occur.

[Embodiment 1]
FIG. 1 is a longitudinal sectional view of a journal bearing 4 formed in a lower part of a cylinder block 2 of an internal combustion engine for a vehicle, in a plane parallel to the axial direction. 2 shows a configuration viewed from the axial direction (the right direction in FIG. 1), and a cross-sectional view taken along line A1-A1 in FIG. 2 corresponds to FIG. The cylinder block 2 of the internal combustion engine is made of an aluminum alloy, and a bearing cap 8 made of an iron alloy is fastened with a bolt 6 to the lower portion thereof. As a result, the journal bearing 4 and the bearing cap 8 rotatably support the journal portion 10a of the crankshaft 10 made of an iron alloy via the bearing metals 12 and 14.

  Grooves 16 and 18 are formed on both axial surfaces of the journal bearing 4 along the bearing inner peripheral surface 4a. Thrust washers 20 and 22 having the same shape are disposed in the grooves 16 and 18, respectively. FIG. 3 shows the shapes of the thrust washers 20 and 22. 3, (A) is a front view, (B) is a left side view, and (C) is a cross-sectional view taken along line A2-A2 in (A).

  The thrust washers 20 and 22 have an arc shape in which a ring-shaped body made of a flat plate is cut in half along the axis. Metal plates 24 and 26 are provided on both axial surfaces of the thrust washers 20 and 22, respectively. The metal plates 24 and 26 are thin spring steel plates, and between these two metal plates 24 and 26, an elastic body that generates local compressive deformation in the thickness direction together with the metal plates 24 and 26, here a resin A rubber material 28 (urethane rubber or the like), which is an elastic body, is laminated in a bonded state to form a laminated steel plate as a metal composite.

  4 and 5 show a state immediately before the bearing cap 8 is combined with the journal bearing 4 of the cylinder block 2. FIG. 6 shows a state immediately after the combination, in which the bolt is not yet fastened. Therefore, the journal bearing 4 of the cylinder block 2 is not distorted by bolt fastening.

  When the bearing cap 8 is fixed to the lower portion of the cylinder block 2 by bolting as shown in FIGS. 1 and 2, the axial direction of the grooves 16 and 18 on the journal bearing 4 side, particularly on the side in contact with the bearing cap 8. A deformed portion 4b due to distortion is generated outward. As a result, the thrust washers 20 and 22 are partially pushed toward the crankshaft 10 near the bearing cap 8.

  Both the front and back surfaces of the thrust washers 20 and 22 are covered with metal plates 24 and 26, respectively, but the inside is a flexible rubber material 28 rich in elasticity. Therefore, as shown in FIG. 1, even if the metal plates 24 and 26 are locally pushed toward the rubber material 28 by the deformable portion 4b, the rubber material 28 is locally compressed and deformed in the thickness direction corresponding to this pressure. Produce. Thus, the internal rubber member 28 flexibly responds to disperse the pressing force from the deforming portion 4b over a wide range of the metal plates 24 and 26 on the side opposite to the deforming portion 4b. As a result, it is possible to suppress the deformation of the metal plates 24 and 26 on the side opposite to the deforming portion 4b from locally protruding in the axial direction.

  Here, as a conventional example, instead of the thrust washers 20 and 22 shown in FIG. 3, a conventional thrust washer Y1 formed entirely of only a metal material (including a laminate of a plurality of metals) as shown in FIG. As shown in FIG. 16, the same arrangement as in FIG. 1 was performed. 15A is a front view, FIG. 15B is a left side view, and FIG. 15C is a sectional view taken along line XX in FIG. Here, the main body Y1a of the thrust washer Y1 is a steel plate, and an aluminum lining layer Y1b is formed on the sliding surface side. Further, a notch-shaped relief portion Y1c is formed in advance corresponding to the deformed portion 4b of the grooves 16 and 18 on the journal bearing 4 side.

  The configuration of FIG. 1 and the configuration of FIG. 16 are applied to an L-type four-cylinder diesel engine, respectively, and a continuous high-speed durability test (300 hours) is performed. The thrust washers 20 and 22 of the present embodiment and the conventional type The durability with the thrust washer Y1 was evaluated. As a result, in the thrust washers 20 and 22 of the present embodiment, the sliding surface fatigue peel area was 0% with respect to the entire sliding surface, but 15% in the conventional thrust washer Y1. That is, the conventional thrust washer Y1 does not sufficiently correspond to the shape of the deformed portion 4b that actually occurs even if the relief portion Y1c is formed in advance.

In the above-described configuration, all the layers of the two metal plates 24 and 26 and the rubber material 28 correspond to the compression deformation portion in relation to the claims.
According to the first embodiment described above, the following effects can be obtained.

  (I). As described above, the thrust washers 20 and 22 according to the present embodiment are provided with compression deformation portions formed by sandwiching the rubber material 28 between the metal plates 24 and 26. As a result, even if local axial pressure is generated from the opposed surfaces 16a and 18a, which are the bottom surfaces of the grooves 16 and 18 on the journal bearing 4 side, due to the generation of the deformed portion 4b, the local thickness corresponding to this is generated. It absorbs by generating a compressive deformation in the vertical direction.

  As a result, the pressure is transmitted to the opposed surface 10b side of the crankshaft 10 in a widely dispersed manner. Accordingly, it is possible to suppress a local pressure increase on the sliding surface, here, the surfaces of the metal plates 24 and 26 on the crankshaft 10 side. Thus, the absorbability with respect to the deformation | transformation of the journal bearing 4 after an assembly | attachment can be improved, and the friction and abrasion by a local part can be suppressed.

  Moreover, since the sliding surface side is one of the metal plates 24 and 26 and is made of a metal material, the durability is high and peeling and cracking are unlikely to occur. Since both sides of the thrust washers 20 and 22 are made of a metal material, the durability is particularly high and peeling and cracking are less likely to occur.

  (B). In the crankshaft support structure of the present embodiment, no thrust washer is provided between the axially opposed surfaces of the crankshaft 10 and the bearing cap 8 of the internal combustion engine. Only the thrust washers 20 and 22 are disposed between the axially opposed surfaces of the crankshaft 10 and the journal bearing 4.

  In the case of such a type, as described above, the deformed portion 4b is generated by bolt fastening, and the thrust washers 20 and 22 are likely to be locally hit after assembly. However, as described above, the thrust washers 20 and 22 used in this crankshaft support structure enhance the absorbability against deformation of the journal bearing 4 after assembly. Therefore, even in this type of crankshaft support structure, friction and wear due to local contact can be effectively suppressed, durability is high, and peeling and cracking are unlikely to occur.

  (C). Since the rubber members 28 are flexible in the thrust washers 20 and 22, the axial pressure generated when the clutch is engaged can be absorbed, and the N / V ratio can be reduced to improve fuel efficiency. .

  (D). The thrust washers 20 and 22 of the present embodiment do not require the processing of the relief portion Y1c and are made of an iron alloy, compared to the conventional thrust washer Y1 formed only of the metal material shown in FIGS. The difference in thermal expansion between the crankshaft 10 and the cylinder block 2 made of aluminum alloy can be sufficiently absorbed.

[Embodiment 2]
In the present embodiment, a thrust washer 120 shown in FIG. 7 is used instead of the thrust washers 20 and 22 shown in FIG. 7A is a front view, FIG. 7B is a left side view, and FIG. 7C is a sectional view taken along line A3-A3 in FIG.

  The overall circular arc shape of the thrust washer 120 is the same as that of the thrust washers 20 and 22. However, the two metal plates 124 and 126 on the front and back surfaces are both formed of corrugated sheet spring steel plates. This is different from the case of the first embodiment. Other configurations are the same as those of the first embodiment. Therefore, it demonstrates with reference to FIGS.

  In the thrust washer 120 having such a configuration, since the metal plates 124 and 126 are more flexible, the metal plates 124 and 126 on the deformed portion 4b side can be flexibly accommodated together with the internal rubber material 128. For this reason, the pressing force from the deformation part 4b can be distributed over a wide range of the metal plates 124 and 126 on the side opposite to the deformation part 4b. As a result, it is possible to suppress the deformation of the metal plates 124 and 126 on the side opposite to the deforming portion 4b protruding locally in the axial direction.

  7 using the thrust washer 120 of FIG. 7 and the configuration of FIG. 16 applied to an L-type four-cylinder diesel engine, respectively, and the continuous high-speed durability test performed in the first embodiment. (300 hours). As a result, in the thrust washer 120 of the present embodiment, the sliding surface fatigue peel area was 0% with respect to the entire sliding surface, but as described above, it was 15% in the conventional thrust washer Y1.

In the above-described configuration, the relationship with the claims is that all layers of the two metal plates 124 and 126 and the rubber material 128 correspond to the compression deformation portion.
According to the second embodiment described above, the following effects can be obtained.

  (I). The same effect as in the first embodiment can be produced. In particular, the thrust washer 120 of the present embodiment is highly flexible with respect to the two metal plates 124 and 126, so that it is possible to further improve the absorbability against deformation of the journal bearing 4 after assembly, Friction and wear due to can be effectively suppressed.

[Embodiment 3]
In the present embodiment, a thrust washer 220 shown in FIG. 8 is used instead of the thrust washers 20 and 22 shown in FIG. 8A is a front view, FIG. 8B is a perspective view, and FIG. 8C is a right side view. The overall arc shape of the thrust washer 220 is the same as that of the thrust washers 20 and 22, but in the case of the first embodiment, one thin spring steel plate is formed in a corrugated shape along the arc. And different. Further, a solid lubricant film is formed on one surface of the thrust washer 220, here the surface to be brought into contact with the opposing surface 10b of the crankshaft 10 shown in FIG. Examples of the solid lubricating coating include MoS2 coating, graphite-resin coating, and Ni-PTFE plating coating. A solid lubricating film may be formed on both surfaces of the thrust washer 220.

Other configurations are the same as those of the first embodiment. Therefore, it demonstrates with reference to FIGS.
Since the thrust washer 220 having such a configuration is highly flexible even if it is entirely made of a metal material, the thrust force from the deforming portion 4b is dispersed and absorbed in the thrust washer 220. As a result, it is possible to suppress deformation in which the side opposite to the deforming portion 4b protrudes in the axial direction locally.

  8 using the thrust washer 220 of FIG. 8 and the configuration of FIG. 16 applied to an L-type four-cylinder diesel engine, respectively, and the continuous high-speed durability test performed in the first embodiment. (300 hours). As a result, in the thrust washer 220 of the present embodiment, the sliding surface fatigue peel area was 0% with respect to the entire sliding surface, but as described above, it was 15% in the conventional thrust washer Y1.

In the configuration described above, the entire thrust washer 220 corresponds to the compression deformation portion in relation to the claims.
According to the third embodiment described above, the following effects can be obtained.

(I). Even if the thrust washer 220 is formed of only a metal material, the same effect as in the first embodiment can be produced.
[Embodiment 4]
In the present embodiment, a thrust washer 320 shown in FIG. 9 is used instead of the thrust washers 20 and 22 shown in FIG. 9A is a front view, FIG. 9B is a perspective view, and FIG. 9C is a right side view. The overall arc shape of the thrust washer 320 is the same as that of the thrust washers 20 and 22, but a single steel plate 324 is formed in an arc shape to determine the overall shape. A paper lining layer 326 is partially bonded to the front and back surfaces of the steel plate 324. For example, an epoxy resin is used as the adhesive. The thrust washer 320 is incorporated as shown in FIG. Since the configuration other than the thrust washer 320 in FIG. 10 is the same as that of the first embodiment, the same configuration is denoted by the same reference numeral.

  As shown in FIG. 10, the paper lining layer 326 in the steel plate 324 is bonded to avoid the deformed portion 4b. That is, the paper lining layer 326 is laminated on at least the surface of the steel plate 324, which is a metal support plate, on the side that receives the local axial pressure by the deformable portion 4b. In the same plane, the paper lining layer 326 does not exist in a region that receives a local axial pressure from the deformable portion 4b. Therefore, the thrust washer 320 does not receive a strong axial pressure from the deforming portion 4b, and can suppress the deformation that the side opposite to the deforming portion 4b locally protrudes in the axial direction.

  The configuration of FIG. 10 and the configuration of FIG. 16 were each applied to an L-type four-cylinder diesel engine, and the continuous high-speed durability test (300 hours) performed in the first embodiment was performed. As a result, in the thrust washer 320 of the present embodiment, the sliding surface fatigue peel area was 0% with respect to the entire sliding surface, but as described above, it was 15% in the conventional thrust washer Y1.

According to the fourth embodiment described above, the following effects can be obtained.
(I). The thrust washer 320 of the present embodiment is not provided with the paper lining layer 326 in the region that receives the local axial pressure. As a result, even when the deforming portion 4b that transmits the pressure in the local axial direction is generated from the opposing surface, the protrusion of the deforming portion 4b can be absorbed. From this, it becomes possible to suppress a local pressure increase on the sliding surface, here, the surface of the paper lining layer 326 on the facing surface 10b side of the crankshaft 10. Therefore, the absorbability with respect to the deformation | transformation of the journal bearing 4 after an assembly | attachment can be improved, and the friction and abrasion by a local part can be suppressed.

  As a result, as shown in FIG. 10, even if the crankshaft support structure is constituted by the thrust washer 320 in which the paper lining layer 326 is disposed on the sliding surface side, the thrust washer 320 has high durability and is hardly peeled off or cracked.

[Embodiment 5]
The crankshaft support structure of the present embodiment is as shown in FIGS. FIG. 11 is a longitudinal sectional view of a journal bearing 404 formed in the lower part of the cylinder block 402 of the vehicle internal combustion engine, in a plane parallel to the axial direction. 12 shows a configuration viewed from the axial direction (the right direction in FIG. 11), and a cross-sectional view taken along line A4-A4 in FIG. 12 corresponds to FIG. A bearing cap 408 is fastened to the lower portion of the cylinder block 402 of the internal combustion engine by bolts 406, whereby the journal bearing 404 and the bearing cap 408 connect the journal portion 410 a of the crankshaft 410 to the bearing metals 412 and 414. It is supported so as to be able to rotate through.

  In the present embodiment, as shown in the first embodiment, grooves 416 and 418 are formed on both axial surfaces of the journal bearing 404 along the bearing inner peripheral surface 404a. Thrust washers 420 and 422 having the same shape are arranged in the grooves 416 and 418, respectively. FIG. 13 shows the shapes of the thrust washers 420 and 422. 13A is a front view, FIG. 13B is a left side view, and FIG. 13C is a cross-sectional view taken along line A5-A5 in FIG.

  The thrust washers 420 and 422 have a circular arc shape obtained by cutting a ring-shaped body made of a flat plate in half along an axis, and are entirely made of a metal material. In addition, you may use the thrust washer of the structure as the said Embodiment 1-4.

  In the present embodiment, on the bearing cap 408 side, grooves 417 and 419 are formed on both axial surfaces along the bearing inner peripheral surface 408a. Concave portions 417b and 419b are formed in the radial direction at the lowermost portions of these grooves 417 and 419.

  Thrust washers 421 and 423 having the same shape are arranged in the grooves 417 and 419, respectively. FIG. 14 shows the shapes of the thrust washers 421 and 423. 14A is a front view, FIG. 14B is a left side view, and FIG. 14C is a cross-sectional view taken along line A6-A6 in FIG.

  The thrust washers 421 and 423 have a circular arc shape obtained by cutting a ring-shaped body made of a flat plate in half along the axis, and further, protrusions 421a and 423a are formed in the radial direction at the lowermost portion. Metal plates 424 and 426 are provided on both surfaces in the axial direction of the thrust washers 421 and 423. The metal plates 424 and 426 are thin plate spring steel plates, and an elastic material is provided between the two metal plates 424 and 426. A body, here, a rubber material 428 such as urethane rubber is laminated in a bonded state to form a laminated steel plate as a metal composite. That is, the laminated structure is the same as the thrust washer of the first embodiment. In addition, you may use the thrust washer of the structure like the said Embodiment 2-4 instead of such a laminated structure. In the case of the configuration of the fourth embodiment (FIG. 9), the paper lining layer is not disposed in the peripheral region of the lowermost protrusions 421a and 423a.

  The opposed surfaces 416a and 418a on the journal bearing 404 side with respect to the opposed surface 410b of the crankshaft 410 and the opposed surfaces 417a and 419a on the bearing cap 408 side with respect to the opposed surface 410b of the crankshaft 410 are the same in the state where they are fastened with bolts. Finished on a flat surface. Therefore, even if the thrust washers 420 and 422 are assembled as shown in FIGS. 11 and 12 and the bearing cap 408 is fastened to the cylinder block 402 with the bolt 406, as shown in the first to fourth embodiments (FIGS. 1 and 10). The deformed portion 4b does not protrude. Therefore, the thrust washer 420, 422 on the journal bearing 404 side does not cause friction or wear due to local contact even with the configuration shown in FIG.

  The bearing cap 408 is bolted to the tip of the journal bearing 404 at two points. For this reason, the lowermost end portion of the bearing cap 408 causes vibration deformation in the axial direction due to vibration during operation of the internal combustion engine. In the present embodiment, since the thrust washers 421 and 423 are also arranged on the bearing cap 408 side, when the deformation due to vibration generated in the bearing cap 408 becomes large, the thrust washers 421 and 423 are particularly arranged at the lower end portion thereof. Thus, the local contact occurs with respect to the opposing surface 410b of the crankshaft 410. That is, the periphery of the lowermost protrusions 421a and 423a is pressed against the opposing surface 410b side of the crankshaft 410 by the opposing surfaces 417a and 419a on the bearing cap 408 side. That is, the same phenomenon as that caused by local deformation by the deforming portion 4b described in the first embodiment is caused by vibration.

  However, the front and back surfaces of the thrust washers 421 and 423 are covered with metal plates 424 and 426, respectively, but the inside is a flexible rubber material 428 rich in elasticity. For this reason, even if the metal plates 424 and 426 are locally pressed by the axial vibration deformation of the bearing cap 408, the internal rubber material 428 is locally compressed and deformed in the thickness direction corresponding to this pressure. Thus, the internal rubber material 428 flexibly responds to disperse the pressing force from the front end side of the bearing cap 408 over a wide range of the metal plates 424 and 426 on the facing surface 410b side of the crankshaft 410. As a result, deformation of the metal plates 424 and 426 locally protruding in the axial direction can be suppressed.

In the above-described configuration, all the layers of the two metal plates 424 and 426 and the rubber material 428 correspond to the compression deformation portion in relation to the claims.
According to the fifth embodiment described above, the following effects can be obtained.

  (I). As described above, even in the crankshaft support structure using the four thrust washers 420, 421, 422, and 423, the thrust washers 421 and 423 on the bearing cap 408 side absorb the vibration deformation in the axial direction of the bearing cap 408. Is increasing. For this reason, friction and wear due to local contact can be suppressed, durability is high, and peeling and cracking are unlikely to occur.

(B). For the thrust washers 421 and 423 on the bearing cap 408 side, the same effects can be produced even if the configurations of the second to fourth embodiments are adopted.
[Other embodiments]
(A). In the first embodiment (FIGS. 1 to 6), the thrust washers 20 and 22 have two metal plates 24 and 26 on both sides of the rubber material 28. Instead of this, a metal plate may be provided only on the facing surface 10b side of the sliding crankshaft 10, and the rubber material 28 may be in direct contact with the facing surfaces 16a and 18a of the journal bearing 4 that does not slide. The same applies to the second embodiment (FIG. 7).

  (B). In the second embodiment (FIG. 7), the entire two metal plates 124 and 126 are formed in a corrugated shape. However, the corrugated shape may be used only in the vicinity of the portion where the deformed portion 4b is generated. .

The two metal plates 124 and 126 may not be corrugated, but the deformed portion 4b (FIG. 1) side may be corrugated and the opposing surface 10b side of the crankshaft 10 may be flat.
(C). In Embodiment 4 (FIGS. 9 and 10), the paper lining layer 326 is provided on both surfaces of the thrust washer 320, but it may be provided only on the surface on the deformed portion 4b side.

  In addition, the paper lining layer 326 is not provided in the region corresponding to the deformed portion 4b, and the local contact from the deformed portion 4b is eliminated or reduced. However, the paper lining layer 326 in the corresponding region is formed thinly so as to be locally formed. It is possible to eliminate or reduce the number of hits.

  Further, even if the paper lining layer 326 is provided on the entire surface of the deformable portion 4b side, the flexibility of the paper lining layer 326 can eliminate or reduce the local contact from the deformable portion 4b. In addition, the durability can be improved.

  (D). In the thrust washer 220 of the third embodiment, a solid lubricant film is formed on at least the surface to be brought into contact with the opposed surface 10b of the crankshaft 10, but at least the opposed surface 10b of the crankshaft 10 is also applied to the first, second, and fifth embodiments. A solid lubricating film may be formed on the surface to be brought into contact with.

In the third embodiment, if the thin spring steel plate itself has high lubricity, it is not necessary to form a solid lubricant film.
Further, the thrust washer 220 of the third embodiment may be corrugated only in the vicinity of the portion where the deformed portion 4b is generated. This can prevent the corrugated plate portion from flexibly responding to the pressure of the deforming portion 4b being transmitted to the sliding surface as it is.

  Conversely, the thrust washer 220 of the third embodiment may be corrugated only in a region other than the portion where the deformable portion 4b occurs. As a result, a flat plate-like portion having a small thickness without being bent even in the thrust washer 220 is positioned in the deformed portion 4b. As a result, the pressure of the deforming portion 4b is prevented from being transmitted, or even if it is transmitted, the pressure is transmitted to the sliding surface via the corrugated plate portion, so that the pressure of the deforming portion 4b is transmitted to the sliding surface as it is. Can be prevented.

  (E). In each of the above embodiments, since the field relates to the bearing of the crankshaft of the internal combustion engine, the thrust washer is installed on the journal bearing or the bearing cap side. On the contrary, when a thrust washer is installed on the shaft side in a mechanism in which the shaft side is fixed and the bearing side rotates, a deformed portion may occur due to vibration or fastening on the shaft side. Even in this case, by applying the present invention, it is possible to increase the absorbability with respect to the deformation on the shaft side after assembly, thereby suppressing friction and wear due to local contact and enhancing durability.

FIG. 3 is a longitudinal sectional view of a peripheral portion of the internal combustion engine journal bearing according to the first embodiment. The right view in the structure of FIG. FIG. 3 is a configuration explanatory diagram of a thrust washer according to the first embodiment. FIG. 3 is an explanatory diagram of assembly of a thrust washer according to the first embodiment. The right view in the structure of FIG. The state explanatory drawing immediately after the combination of the journal bearing and bearing cap in Embodiment 1. FIG. FIG. 4 is a configuration explanatory diagram of a thrust washer according to a second embodiment. FIG. 6 is a configuration explanatory diagram of a thrust washer according to a third embodiment. FIG. 6 is a configuration explanatory diagram of a thrust washer according to a fourth embodiment. The thrust washer assembly explanatory drawing of Embodiment 4. FIG. FIG. 10 is a longitudinal sectional view of a peripheral portion of an internal combustion engine journal bearing according to a fifth embodiment. The right view in the structure of FIG. FIG. 6 is a configuration explanatory diagram of a thrust washer according to a fifth embodiment. FIG. 6 is a configuration explanatory diagram of a thrust washer according to a fifth embodiment. The structure explanatory drawing of the thrust washer of a prior art example. The longitudinal cross-sectional view in the peripheral part of the internal combustion engine journal bearing of a prior art example.

Explanation of symbols

  2 ... Cylinder block, 4 ... Journal bearing, 4a ... Bearing inner peripheral surface, 4b ... Deformed part, 6 ... Bolt, 8 ... Bearing cap, 10 ... Crankshaft, 10a ... Journal part, 10b ... Opposing surface, 12, 14 ... Bearing metal, 16, 18 ... groove, 16a, 18a ... opposite surface, 20, 22 ... thrust washer, 24, 26 ... metal plate, 28 ... rubber material, 120 ... thrust washer, 124, 126 ... metal plate, 128 ... rubber 220, thrust washer, 320 ... thrust washer, 324 ... steel plate, 326 ... paper lining layer, 402 ... cylinder block, 404 ... journal bearing, 404a ... bearing inner peripheral surface, 406 ... bolt, 408 ... bearing cap, 408a ... bearing inner peripheral surface, 410 ... crankshaft, 410a ... journal portion, 410b ... pair Surface, 412, 414 ... Bearing metal, 416, 418 ... Groove, 416a, 418a ... Opposing surface, 417, 419 ... Groove, 417a, 419a ... Opposing surface, 417b, 419b ... Recess, 420, 421, 422, 423 ... Thrust Washers, 421a, 423a ... projections, 424, 426 ... metal plate, 428 ... rubber material.

Claims (10)

A thrust washer disposed between axially opposed surfaces of a shaft and a bearing,
The sliding surface side with respect to one of the opposing surfaces is made of a metal material, and a compression deformation portion is formed that causes local compressive deformation in the thickness direction in response to local axial pressure from the other of the opposing surfaces. Thrust washer characterized by 2. The thrust washer according to claim 1, wherein the compression deformation portion is formed of a metal composite in which a resin elastic body is disposed between two metal plates. 3. The thrust washer according to claim 2, wherein one or both of the two metal plates are spring steel plates and are formed in a corrugated plate shape. The thrust thrust washer according to claim 1, wherein the entire thrust washer is made of a single spring steel plate, and the compression deformation portion is formed by forming a part or all of the spring steel plate into a corrugated plate shape. Washer. A thrust washer disposed between axially opposed surfaces of a shaft and a bearing,
A thrust washer, characterized in that a paper lining layer is provided on a surface of the metal support plate on the side that receives at least local axial pressure. 6. The thrust washer according to claim 5, wherein a paper lining layer is thinned or not provided in a region of the surface which receives a local axial pressure. 7. The thrust washer according to claim 1, wherein the shaft is a crankshaft of an internal combustion engine, and the bearing is a journal bearing or a bearing cap of a cylinder block. The thrust washer according to any one of claims 1 to 7, wherein a solid lubricating film is formed on a sliding surface with respect to one of the opposing surfaces. 9. A thrust washer is not provided between the axial facing surfaces of the crankshaft and the bearing cap of the internal combustion engine, and the axial facing surfaces of the crankshaft and the journal bearing of the cylinder block are any one of claims 1-8. A crankshaft support structure, characterized in that the thrust washer described in 1 is disposed. The thrust washer is provided between the axial facing surfaces of the crankshaft of the internal combustion engine and the journal bearing of the cylinder block, and the axially facing surfaces of the crankshaft and the bearing cap are according to any one of claims 1 to 8. Crankshaft support structure, characterized in that a thrust washer is arranged.

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