JP6844039B2 - Thrust washer - Google Patents

Description

The present invention relates to a thrust washer.

In mechanical devices such as clutch devices, gear mechanisms, compressors, etc., thrust washers as shown in Patent Documents 1 to 4 may be attached. The thrust washer disclosed in Patent Document 1 is formed so that an oil groove faces from the insertion hole to the outer peripheral side. Further, the thrust washer disclosed in Patent Document 2 includes a first oil passage that communicates the inner peripheral surface and the outer peripheral surface of the thrust washer, and a dead-end second oil that opens on the inner peripheral surface but does not open on the outer peripheral surface. There is a road.

Further, the thrust washer disclosed in Patent Document 3 is provided with an arc-shaped refueling groove and a V-shaped refueling groove. Further, the thrust washer disclosed in Patent Document 4 has a first oil groove and a second oil groove extending from the inner peripheral edge to the outer peripheral edge, and a communicating oil groove for communicating the first oil groove and the second oil groove. The configuration is disclosed.

Japanese Patent No. 4370982 JP-A-2007-16931 Japanese Patent No. 5727909 Japanese Unexamined Patent Publication No. 2015-152061

Although the thrust washer has a mating material facing each other, lubricating oil is interposed between the thrust washer and the mating material. Under such an environment, the lubrication state of the thrust washer is assumed to be in the mixed lubrication region in the Strivec diagram, and although the thrust washer is partially separated from the mating material by the oil film of the lubricating oil, one It is considered that the thrust washer is in direct contact with the mating material. In such a mixed lubrication region, it is not known in detail what kind of thrust washer configuration should be used to reduce the sliding load. On the other hand, in recent years, thrust washers are further required to reduce the sliding load on the sliding surface. Therefore, it is required to reduce the sliding load even higher than the thrust washers disclosed in Patent Documents 1 to 4 described above.

The present invention has been made based on the above circumstances, and an object of the present invention is to provide a thrust washer capable of reducing a sliding load.

In order to solve the above problems, according to the first aspect of the present invention, the thrust washer is made of a material containing a resin having a ring-shaped portion surrounding the insertion hole, and the thrust washer has a ring-shaped portion on the surface. A sliding surface that slides with other members is provided on the back surface, and an oil groove that is recessed from the sliding surface and allows lubricating oil to enter is provided on at least one of the front surface and the back surface, and a hole that penetrates the ring-shaped portion is provided. The surface and the back surface are closed by a ring-shaped portion without being formed, and the oil groove is recessed from the sliding surface and has an opening that allows lubricating oil to enter from the insertion hole side. Lubricating oil that exists on the inner peripheral end side of the ring-shaped portion and has entered the oil groove while separating the oil groove and the outer side of the ring-shaped portion at the outer peripheral end portion of the ring-shaped portion of at least one oil groove. An oil stop wall is provided to prevent the oil from flowing out to the outer peripheral side of the ring-shaped portion, and the position of the oil stop wall in the thickness direction of the thrust washer is provided at the same position as the sliding surface. Provided is a thrust washer characterized in that the sliding area ratio occupied by the sliding surface with respect to the projected surface in the plan view of the ring-shaped portion is provided in the range of 60 to 85%.

Further, another aspect of the present invention is the above-mentioned invention at the intersection position where the center line of the oil groove and the center line passing through the center between the inner peripheral end portion and the outer peripheral end portion of the ring-shaped portion intersect. It is preferable that the inclination angle formed by the center line of the oil groove with respect to the radial line passing through the intersection position and along the radial direction of the ring-shaped portion is provided in the range of 30 degrees to 55 degrees.

Further, another aspect of the present invention is that, in the above-described invention, the oil groove guides the lubricating oil that has entered the oil groove to the sliding surface, and the dynamic pressure is applied between the sliding surface and the other member. It is preferable that the dynamic pressure guide wall surface for causing the above-mentioned is provided adjacent to each other.

Further, another aspect of the present invention is that, in the above-described invention, the oil groove includes a first oil groove that is inclined to one side with respect to the radial direction of the ring-shaped portion and a radial portion of the ring-shaped portion. It is preferable that the second oil groove is provided on the other side, which is different from the one side, and the first oil groove and the second oil groove are connected by an opening.

Further, as for another aspect of the present invention, in the above-described invention, the first oil groove and the second oil groove are each provided with a bottom portion recessed most from the sliding surface, and are connected by an opening . the oil groove and a second oil groove, a portion surrounded by the first oil groove and the second oil grooves being connected with said opening in the width direction of the first oil groove inner and second oil groove When it is the inside in the width direction, the part located on the inside and the outside on the opposite side in the width direction of the first oil groove, and the part located on the inside and the outside on the opposite side in the width direction of the second oil groove, It is preferable that the tapered wall surface is provided so as to be linearly inclined toward the sliding surface, and the tapered wall surface is provided wider than the bottom portion.

Further, another aspect of the present invention is that, in the above-mentioned invention, the first oil groove and the second oil groove have a curved wall surface that is curved so as to have an inflection point from the bottom toward the sliding surface. It is preferable that it is provided.

Further, another aspect of the present invention is that, in the above-described invention, the oil groove has a non-communication oil groove separated from the outside of the ring-shaped portion by an oil stop wall and a ring-shaped portion without the oil stop wall. It is preferable that a communication oil groove communicating with the outside of the is provided.

Further, as for another aspect of the present invention, in the above invention, it is preferable that the non-communication oil groove and the communication oil groove are alternately provided in the circumferential direction of the ring-shaped portion.

Further, another aspect of the present invention is that, in the above-described invention, the communicating oil groove is between an adjacent communication oil groove provided adjacent to the non-communication oil groove and a non-communication oil groove separated from each other. It is preferable that an intermediate communication oil groove existing in the above is provided.

Further, another aspect of the present invention is that, in the above-described invention, the oil groove has a non-communication oil groove separated from the outside of the ring-shaped portion by an oil stop wall and a ring-shaped portion without the oil stop wall. There is a communication oil groove that communicates with the outside of the ring-shaped portion, and the communication oil groove is an opening that is adjacent to each other in the circumferential direction of the ring-shaped portion without interfering with the first oil groove and the second oil groove. It is preferably arranged in the intervening part.

Further, another aspect of the present invention is that, in the above-described invention, the non-communication oil groove is provided with a wide groove portion and a narrow groove portion having a groove width narrower than that of the wide groove portion. It is preferable that the wide groove portion is connected to the opening portion and is continuous with the narrow groove portion and is provided on the oil stop wall side.

Further, it is preferable that another aspect of the present invention is provided with an intermediate communication oil groove that communicates with the outside in the above-mentioned invention.

Further, as for another aspect of the present invention, in the above-described invention, an oil scooping surface for guiding the lubricating oil to the opening is provided on the inner peripheral side of the ring-shaped portion, and the oil scooping surface is a ring. It is preferable that the shaped portion is provided so as to be inclined with respect to the axial direction, and the opening is formed by recessing the oil scooping surface.

Further, in the other aspect of the present invention, in the above invention, the height from the inner peripheral end portion of the oil scooping surface to the sliding surface is from the bottom of the oil groove, which is the most recessed from the sliding surface, to the sliding surface. It is preferable that the size is twice or more the height of the above.

Further, as for another aspect of the present invention, in the above-described invention, the ring-shaped portion is provided with an oil introduction groove recessed from the inner diameter side to the outer diameter side of the ring-shaped portion. The inclination angle formed by the bottom of the groove with respect to the axial direction of the ring-shaped portion is smaller than the inclination angle formed by the oil scooping surface with respect to the axial direction, and is provided between the oil introduction groove and the oil scooping surface. It is preferable that a step is provided.

Further, in the other aspect of the present invention, in the above-described invention, at least a part of the boundary wall with the oil scooping surface of the oil introduction groove is provided so as to be inclined with respect to the radial direction of the ring-shaped portion. , Is preferable.

According to the present invention, it is possible to provide a thrust washer capable of reducing the sliding load.

It is a perspective view which shows the structure of the combination thrust washer which concerns on one Embodiment of this invention. It is a top view which shows the structure of the resin thrust washer which comprises the combination thrust washer shown in FIG. 1, and is the figure which shows the state which the oil groove is composed of the non-communication oil groove and the communication oil groove. It is a top view which shows the structure of the resin thrust washer which constitutes the combination thrust washer shown in FIG. 1, and is the figure which shows the structure which two oil grooves having different inclination angles are connected by the opening. It is a partial plan view which shows the structure of the resin thrust washer which concerns on 1st structural example. It is sectional drawing which shows the state which cut the oil groove shown in FIG. 4 along the width direction. It is a top view which shows the structure of the resin thrust washer which concerns on the modification of the 1st structure example. It is a top view which shows the structure of the resin thrust washer which concerns on the modification of the 1st structure example. It is sectional drawing which shows the state which cut the oil groove shown in FIG. 6 along the width direction. It is sectional drawing which shows the state which cut the non-communication oil groove in the width direction of the oil groove shown in FIG. 7. FIG. 5 is a cross-sectional view showing a state in which the communicating oil groove is cut along the width direction among the oil grooves shown in FIG. 7. It is a top view which shows the structure of the resin thrust washer which concerns on 2nd structural example. It is a partial plan view which shows the structure of the resin thrust washer which concerns on 2nd structural example. 11 is a cross-sectional view showing a state in which the oil groove shown in FIGS. 11 and 12 is cut along the width direction. It is a top view which shows the structure of the resin thrust washer which concerns on 3rd structural example. It is a partial plan view which shows the structure of the resin thrust washer which concerns on 3rd structural example. It is sectional drawing which shows the state which cut the oil groove shown in FIG. 14 and FIG. 15 along the width direction. It is a partial plan view which shows the structure of the resin thrust washer which concerns on 4th structural example. It is sectional drawing which shows the state which cut the oil groove shown in FIG. 3 and FIG. 17 along the width direction. It is a partial plan view which shows the structure of the resin thrust washer which concerns on 5th structural example. It is sectional drawing which shows the state which cut the oil groove shown in FIG. 19 along the width direction. It is a partial plan view which shows the structure of the resin thrust washer which concerns on 6th structural example. It is sectional drawing which shows the state which cut the oil groove shown in FIG. 21 along the width direction. It is a partial plan view which shows the structure of the resin thrust washer which concerns on 7th structural example. FIG. 3 is a cross-sectional view showing a state in which the oil groove shown in FIG. 23 is cut along the width direction. It is a partial plan view which shows the structure of the resin thrust washer which concerns on 8th structural example. FIG. 5 is a cross-sectional view showing a state in which the oil groove shown in FIG. 25 is cut along the width direction. It is a partial plan view which shows the structure of the resin thrust washer which concerns on 9th structural example. It is sectional drawing which shows the state which cut the oil groove shown in FIG. 27 along the width direction. It is a partial plan view which shows the structure of the resin thrust washer which concerns on 11th structural example. FIG. 5 is a cross-sectional view showing a state in which the oil groove shown in FIG. 29 is cut along the width direction. It is a partial cross-sectional view which shows the state which cut the resin thrust washer along the radial direction, and has enlarged the vicinity of the oil scooping surface. It is sectional drawing which shows the schematic structure of the load measuring apparatus. It is a figure which shows the experimental result about the relationship between the sliding area ratio and torque (average torque) of the resin thrust washer which concerns on 1st structural example. It is a figure which shows the experimental result about the relationship between the sliding area ratio and torque (average torque) of the resin thrust washer which concerns on 2nd structural example. It is a figure which shows the experimental result about the relationship between the sliding area ratio and torque (average torque) of the resin thrust washer which concerns on 4th structural example. It is a top view which shows the structure of the resin thrust washer which concerns on the modification of the 12th structure example. It is a top view which shows the structure of the resin thrust washer which concerns on the modification of the thirteenth structure example.

Hereinafter, a resin thrust washer 20 as a thrust washer made of a material containing a resin and a combination thrust washer 10 using the resin thrust washer 20 according to an embodiment of the present invention will be described with reference to the drawings. ..

[1. About the overall configuration of the combination thrust washer 10]
The combination thrust washer 10 is incorporated in, for example, a compressor of a transmission device of a vehicle or an air conditioner device of a vehicle. The configuration of the combined thrust washer 10 is shown in FIG. FIG. 1 is a perspective view showing the configuration of the combined thrust washer 10.

As shown in FIG. 1, the combination thrust washer 10 of the present embodiment includes three thrust washers S1, S2, and S3. The combination thrust washer 10 including the three thrust washers S1, S2 and S3 is located between the mating materials C1 and C2 and is in a state of receiving a load in the thrust direction.

The environment in which the combination thrust washer 10 and the mating materials C1 and C2 are provided is an environment in which lubricating oil is supplied. However, it is estimated from the sliding marks of the thrust washer in various experimental results until reaching the combined thrust washer 10 according to the present embodiment and the sliding load measured by various experimental results, etc., the combined thrust washer 10 The lubrication state of the environment in which is used is assumed to be in the mixed lubrication region in the Stribeck diagram. Therefore, it is presumed that an oil film is present in a part between the thrust washer and the mating material, and a part of the thrust washer is in direct contact with the mating material.

The above-mentioned thrust washers S1, S2, and S3 are selected from (1) resin thrust washers 20 made of resin (see FIGS. 2, 3, etc.) and (2) metal thrust washers made of metal. It is configured to include at least one resin thrust washer 20. Specifically, in the combination thrust washer 10 shown in FIG. 1, the resin thrust washer 20 may be arranged on the mating material C1 side and the mating material C2 side, and the metal thrust washer may be arranged in the center, and the mating material C1 may be arranged. The resin thrust washer 20 may be arranged only on the side and the rest may be a metal thrust washer, or the resin thrust washer 20 may be arranged only on the mating material C2 side and the rest may be a metal thrust washer. Further, a metal thrust washer may be arranged only on the mating material C1 side and the remaining two pieces may be used as a resin thrust washer 20, or a metal thrust washer may be placed only on the mating material C2 side and the remaining two pieces may be made of resin thrust. The washer 20 may be used, or a metal thrust washer may be arranged on both the mating material C1 side and the mating material C2 side, and a resin thrust washer 20 may be arranged in the center. Further, the three thrust washers S1, S2, and S3 described above may all be resin thrust washers 20.

[2. About the composition of the resin thrust washer 20]
First, the configuration of the resin thrust washer 20 constituting the combination thrust washer 10 will be described. FIG. 2 is a plan view showing the configuration of the resin thrust washer 20 constituting the combination thrust washer 10 shown in FIG. 1, and shows a state in which the oil groove 25 is composed of the non-communication oil groove 25a and the communication oil groove 25b. It is a figure. Further, FIG. 3 is a plan view showing the configuration of the resin thrust washer 20 constituting the combination thrust washer 10 shown in FIG. 1, and two oil grooves 25 having different inclination angles are connected by an opening 27. It is a figure which shows the structure. In the configuration shown in FIG. 3, two oil grooves 25 having different inclination angles are connected at the opening 27, so that the entire oil groove 25 has a substantially V-shaped shape.

In the following description, the resin thrust washer 20 having a structure in which one oil groove 25 is not connected to the other oil groove 25 in a substantially V shape as shown in FIG. 2 is referred to as a resin thrust washer 20A. Call it. Further, a resin thrust washer 20 having an oil groove 25 connected so as to draw a substantially V shape as shown in FIG. 3 is referred to as a resin thrust washer 20B. However, when it is not necessary to distinguish between the resin thrust washer 20A and the resin thrust washer 20B, it is simply referred to as the resin thrust washer 20.

The resin thrust washer 20 is made of (1) a resin base material alone, (2) a resin base material mixed with a fiber material, (3) a resin base material mixed with a filler, and (4) a resin. It is either a base material mixed with a fiber material and a filler. Hereinafter, the resin base material, the fiber material, and the filler will be described respectively.

[2.1. About resin base material]
The resin base material is tetrafluoroethylene resin (PTFE), polyamide resin (PA), polyamideimide resin (PAI), polyimide resin (PI), polybenzoimidazole resin (PBI), aromatic polyetherketones (PAEK). , Modified polyetherketone resin, polyphenylene sulfide resin (PPS), liquid crystal polymer, phenol resin, polyethylene resin, polystyrene resin, acrylic resin, acrylonitrile butadiene / styrene resin, polyacetal resin, polycarbonate resin, polyethersulfone resin (PES), It is any one of polyetherimide resins (PEI), or a mixture of a plurality of these selected and mixed (including polymer alloy and copolymerization).

[2.2. About textile materials]
The fiber material is a reinforcing fiber having an average fiber length of, for example, about 0.0001 mm to 5 mm, and the fiber material is made of an inorganic fiber such as a carbon fiber, a glass fiber, or a potassium titanate fiber. , Aramid fiber, fluorine fiber and other organic fibers are used as materials, but the material is not limited to these. Further, at least one fiber material may be selected from the above-mentioned fiber materials, and fiber materials of other materials may be selected and mixed.

When the fiber material is glass fiber, the weight ratio of the mixing ratio per product is preferably 1 to 40% by weight. When the fiber material is carbon fiber or aramid fiber, the weight ratio of the mixing ratio per product is preferably 1 to 45% by weight. When the fiber material is fluorine fiber, the weight ratio of the mixing ratio per product is preferably 5 to 55% by weight. When the fiber material is potassium titanate, the weight ratio of the mixing ratio per product is preferably 0.1 to 5% by weight.

[2.3. About filler]
The filler is any one of ethylene tetrafluoride resin (PTFE), manganese sulfide (MnS), molybdenum disulfide (MoS ₂ ), graphite, calcium carbonate (CaCo ₃ ), titanium oxide, and melamine cyanurate (MCA). , Or a mixture of these selected from a plurality.

[2.4. About the surface treatment of the resin thrust washer 20]
The surface treatment of the resin thrust washer 20 (the surface treatment here includes the surface modification treatment) is a surface modification treatment using epoxysilane (manufactured by Shin-Etsu Silicone Co., Ltd.), and a titanate-based / aluminate-based coupling agent. (Specifically, surface modification treatment using Bisoo (dioctylpyrophosphate) isopropoxytate; Ajinomoto Fine-Techno Co., Ltd .: trade name 38S), Bisoo (dioctylpyrophosphate) oxyacetate titanate; Surface modification treatment using (Techno), product name 55 (Ajinomoto Fine-Techno), acetoalkoxyaluminum diisopropilate product name AL-M; surface modification using Ajinomoto Fine-Techno) However, any one of these, or a plurality of these may be selected to perform surface treatment (surface modification treatment). Further, instead of the above surface treatment (surface modification treatment), a coupling treatment using corona discharge or ion plasma discharge may be performed, and instead of the above surface modification treatment, DLC treatment or Mo coating may be performed. You may try to do. In particular, the DLC treatment is preferable because it is possible to reduce friction and improve wear resistance at the sliding portion.

[3. Specific configuration of resin thrust washer 20A]
(1) First Configuration Example of Resin Thrust Washer 20A The specific configuration of the resin thrust washer 20A will be described below. First, the resin thrust washer 20A according to the first configuration example will be described. As shown in FIG. 2, the resin thrust washer 20A is provided with a ring-shaped portion 21 so as to cover the insertion hole 22. An oil introduction groove 23 for introducing lubricating oil into the oil groove 25 is provided on the inner peripheral side (insertion hole 22 side) of the ring-shaped portion 21, and the oil introduction groove 23 is on the insertion hole 22 side. It is provided in a shape in which the inner peripheral wall is recessed so as to face the outer diameter side. That is, a rotary shaft (not shown) is arranged in the insertion hole 22, but if the oil introduction groove 23 does not exist, the supply of lubricating oil along the rotary shaft is hindered, so that the lubricating oil is supplied to the oil groove 25. There is a risk that it will not be supplied sufficiently. However, the presence of the oil introduction groove 23 makes it possible to satisfactorily introduce the lubricating oil into the oil groove 25.

An oil scooping surface 24 is provided on the inner peripheral side (insertion hole 22 side) of the ring-shaped portion 21. The oil scooping surface 24 is a portion that guides the lubricating oil introduced from the oil introduction groove 23 in the circumferential direction of the ring-shaped portion 21. The oil scooping surface 24 is formed by processing the inner peripheral side of the ring-shaped portion 21 into, for example, a tapered shape or a curved surface shape.

Further, the ring-shaped portion 21 is provided with an oil groove 25. FIG. 4 is a partial plan view showing the configuration of the resin thrust washer 20A according to the first configuration example. As shown in FIGS. 2 and 4, the oil groove 25 is a ring-shaped portion 21 of other members (counterpart materials C1 and C2, other resin thrust washers 20 and metal thrust washers; hereinafter, simply other members. It is provided so as to be recessed from the front surface or the back surface facing the member). In the following description, the front surface and the back surface of the ring-shaped portion 21 are referred to as sliding surfaces 26. In the configuration shown in FIG. 2, an opening 27 that opens on the insertion hole 22 side is provided on the inner diameter side of the oil groove 25. Therefore, lubricating oil is supplied to the oil groove 25 from the insertion hole 22 side.

The oil groove 25 is provided with a non-communication oil groove 25a and a communication oil groove 25b. The outer diameter side of the non-communication oil groove 25a does not communicate with the outer peripheral side of the resin thrust washer 20A (ring-shaped portion 21). That is, on the outer diameter side of the non-communication oil groove 25a, an oil stop wall 28 for suppressing the lubricating oil from flowing out to the outer peripheral side is arranged. The oil stop wall 28 is flush with the sliding surface 26, but the oil stop wall 28 may be provided so as to have a slight height difference with respect to the sliding surface 26. On the other hand, in the communicating oil groove 25b, the oil stop wall 28 does not exist on the outer diameter side of the ring-shaped portion 21, and the lubricating oil can flow freely from the inner diameter side (insertion hole 22 side) to the outer diameter side.

The width of the oil stop wall 28 is preferably in the range of 0.01 mm to 0.1 mm. It is difficult to make the width of the oil stop wall 28 smaller than 0.01 mm in terms of processing accuracy, and when the width of the oil stop wall 28 is made larger than 0.1 mm, the oil stop wall 28 is used. This is because the sliding load has a large effect on the resin thrust washer 20.

Here, the non-communication oil groove 25a and the communication oil groove 25b according to the first configuration example are provided along the radial direction.

In the above-mentioned communicating oil groove 25b, it is possible to increase the flow rate of the lubricating oil passing toward the outer diameter side as compared with the non-communication oil groove 25a. Therefore, it is possible to improve the heat dissipation of the resin thrust washer 20A.

Further, the cross-sectional shape of the oil groove 25 (non-communication oil groove 25a and communication oil groove 25b) described above is configured as shown in FIG. In the configuration shown in FIG. 5, a pair of tapered wall surfaces 252 are provided so as to face the sliding surface 26 side from the bottom portion 251 of the oil groove 25. The tapered wall surface 252 is a portion that is linearly inclined with a predetermined inclination angle with respect to the sliding surface 26. The tapered wall surface 252 may have a portion that is inclined in a curved shape in addition to the straight line.

The oil groove area ratio with respect to the ring-shaped portion 21 is 15 to 40%. So to speak, of the sliding surface 26, the sliding area ratio obtained by subtracting the oil groove area ratio from the ring-shaped portion 21 is 60 to 85%. At this time, as will be described later, the sliding load is in the lowest state.

Here, the sliding area ratio refers to the ratio of the sliding surface 26 to the projected surface in the plan view of the resin thrust washer 20 (ring-shaped portion 21). The oil groove area ratio is the ratio of the projection surface of the resin thrust washer 20 (ring-shaped portion 21) excluding the sliding surface 26 (the portion that does not come into contact with the mating materials C1 and C2). Percentage). Therefore, the oil groove area ratio includes the oil scooping surface 24, the oil groove 25 (non-communicating oil groove 25a and the communicating oil groove 25b), the dynamic pressure guide wall surface 254, and the surrounding portion 111, which are lower than the sliding surface 26. (See FIG. 23) and the like are included.

Further, in the configuration shown in FIG. 2, the total number of the non-communication oil grooves 25a and the communication oil grooves 25b is eight. Moreover, since the non-communication oil grooves 25a and the communication oil grooves 25b are alternately provided in the circumferential direction, the same number of non-communication oil grooves 25a and the communication oil grooves 25b are provided. However, the total number of the non-communication oil grooves 25a and the communication oil grooves 25b is not limited to eight. Examples of such a configuration are shown in FIGS. 6 and 7.

FIG. 6 is a plan view showing the configuration of the resin thrust washer 20A according to the modified example of the first configuration example. In the resin thrust washer 20A shown in FIG. 6, the total number of the non-communicating oil grooves 25a and the communicating oil grooves 25b is 16. Further, FIG. 7 is a plan view showing the configuration of the resin thrust washer 20A according to the modified example of the first configuration example. In the resin thrust washer 20A shown in FIG. 7, the total number of the non-communicating oil grooves 25a and the communicating oil grooves 25b is 32.

Further, the cross-sectional shape of the oil groove 25 (non-communication oil groove 25a and communication oil groove 25b) shown in FIG. 6 is shown in FIG. Similarly to the oil groove 25 shown in FIG. 5, the oil groove 25 shown in FIG. 8 is also provided with a pair of tapered wall surfaces 252 so as to face the sliding surface 26 side from the bottom portion 251. The tapered wall surface 252 is a portion that is linearly inclined with a predetermined inclination angle with respect to the sliding surface 26. The tapered wall surface 252 may have a portion that is inclined in a curved shape in addition to the straight line.

Further, among the oil grooves 25 shown in FIG. 7, the cross-sectional shape of the non-communication oil groove 25a is shown in FIG. Further, among the oil grooves 25 shown in FIG. 7, the cross-sectional shape of the communicating oil groove 25b is shown in FIG. In the configuration shown in FIG. 9, a convex curved surface portion 253 is provided instead of the tapered wall surface 252 as shown in FIGS. 5 and 8. The convex curved surface portion 253 is a convex curved surface connecting the bottom portion 251 and the sliding surface 26, but unlike a substantially S-shaped curved surface (a curved wall surface or the like described later), the cross-sectional shape has no inflection point. Is. In the configuration shown in FIG. 9, the convex curved surface portion 253 is provided in a shape equivalent to, for example, a round chamfer. However, in the convex curved surface portion 253, for example, a linear portion may be partially present or a concave curved surface portion may be partially present in addition to the convex curved surface portion. Further, also in the configuration shown in FIG. 10, the convex curved surface portion 253 is provided as in the configuration shown in FIG.

The oil groove 25 shown in FIGS. 8 and 9 may be configured as follows. That is, the dimensions a2 and a3 and / or the dimensions b2 and b3 of the oil groove 25 may become smaller toward the outer diameter side. At this time, the dimensions a2 and a3 of the oil groove 25 may change linearly (proportional) from the inner diameter side to the outer diameter side, but change linearly (proportional) instead of linearly (proportional). Is also good. Further, the dimensions b2 and b3 of the oil groove 25 change in conjunction with the dimensional change of the dimensions a2 and a3, and the mode of the dimensional change may be any. Further, the dimensions b2 and b3 of the oil groove 25 may be the same as the whole without being linked to the dimensional change of the dimensional a2 and a3, and the dimensional change of the dimensional b2 and b3 may be a part of the dimensional change. It may exist.

Further, the dimensions H2 and H3 corresponding to the depth of the oil groove 25 from the sliding surface 26 may become smaller toward the outer diameter side. At this time, the dimensions H2 and H3 of the oil groove 25 may decrease linearly (proportionally) from the inner diameter side to the outer diameter side, but change linearly (proportional) instead of linearly (proportional). Is also good. Further, both the dimensions a2 and a3 and the dimensions H2 and H3 may become smaller from the inner diameter side to the outer diameter side of the resin thrust washer 20A. However, either the dimensions a2 and a3 and the dimensions H2 and H3 may become smaller from the inner diameter side to the outer diameter side of the resin thrust washer 20A.

The dimensions of each configuration example described below are a4 to a6, a11 to a16, a18, b4 to b6, b11, b13, b15, b16, b18, H4 to H6, H11 to H13, H15, H16, H18, H141, Also in H142, the same dimensional change as described above may occur.

In the resin thrust washer 20A according to the first configuration example, the oil groove area ratio (sliding area ratio) is generally the configuration shown in FIG. 2, the configuration shown in FIG. 6, and the configuration shown in FIG. 7. Are equal.

(2) Second Configuration Example of Resin Thrust Washer 20A Next, the resin thrust washer 20A according to the second configuration example will be described. FIG. 11 is a plan view showing the configuration of the resin thrust washer 20A according to the second configuration example. FIG. 12 is a partial plan view showing the configuration of the resin thrust washer 20A according to the second configuration example. FIG. 13 is a cross-sectional view showing a state in which the oil groove 25 shown in FIGS. 11 and 12 is cut along the width direction.

In the resin thrust washer 20A according to the second configuration example shown in FIGS. 11 and 12, unlike the resin thrust washer 20A according to the first configuration example, the oil groove 25 is composed of the non-communication oil groove 25a. However, the communication oil groove 25b is not provided. However, in the second configuration example, the oil groove 25 may adopt a configuration in which the communicating oil groove 25b is provided together with the non-communication oil groove 25a.

Also in the resin thrust washer 20A according to the second configuration example, the oil groove area ratio is 15 to 40%. So to speak, the sliding area ratio of the sliding surface 26 is 60 to 85%, and as will be described later, the sliding load of the sliding surface 26 is the lowest.

Further, as shown in FIG. 12, the center line L1 in the radial direction (width direction) of the ring-shaped portion 21 passes through the intersection position P1 at the intersection position P1 that intersects the center line L2 of the non-communication oil groove 25a. The angle formed by the center line L2 with respect to the radial line L3 along the radial direction is defined as the inclination angle θ1. If the inclination angle θ1 of the non-communication oil groove 25a is 30 degrees or more as compared with the configuration in which the non-communication oil groove 25a along the radial direction as shown in FIG. 2 or the like exists, the resin thrust washer will be described later. The wear of 20 is reduced, and the sliding load on other members is further reduced. In each of the following configuration examples (for example, the fourth configuration example), the inclination angle formed by the center line L2 with respect to the same line as the radial line L3 at the same position as the above-mentioned intersection position P1 is set as the inclination angle. It may be described as θ1.

Here, when the inclination angle θ1 is larger than 55 degrees, the non-communication oil groove 25a becomes long. In this case, since the oil groove area ratio is a predetermined value within the range of 15 to 40%, the width dimension of the non-communication oil groove 25a becomes smaller by the length of the non-communication oil groove 25a. .. Then, the width of the non-communication oil groove 25a becomes too narrow and the groove shape collapses, or it is necessary to reduce the number of the non-communication oil grooves 25a due to interference with other non-communication oil grooves 25a or the like. Therefore, the inclination angle θ1 is preferably 55 degrees or less. That is, the inclination angle θ1 is preferably 30 degrees or more and 55 degrees or less.

Further, as shown in FIGS. 11 and 12, in the resin thrust washer 20A according to the second configuration example, a pair of tapered wall surfaces 252 are provided so as to face the sliding surface 26 side from the bottom portion 251 of the oil groove 25. Has been done. The tapered wall surface 252 is a portion that is linearly inclined with a predetermined inclination angle with respect to the sliding surface 26, and a portion that is inclined in a curved shape may exist in addition to the linear shape. ..

The resin thrust washer 20A according to the second configuration example may be configured as follows. That is, the oil groove 25 is not limited to a straight line, but may be provided in a curved line, or a straight line and a curved line may be mixed. Further, the dimension a5 and / or the dimension b5 (see FIG. 13) of the oil groove 25 may become smaller toward the outer diameter side. As an example of such a dimension, for example, the dimension a5 of the inner diameter side end of the oil groove 25 is 0.8 mm, and the dimension of the outer diameter side end of the oil groove 25 is 0.03 mm. Is not limited.

Further, the dimension H5 (see FIG. 13) corresponding to the depth of the oil groove 25 from the sliding surface 26 may become smaller toward the outer diameter side. At this time, the dimension H5 of the oil groove 25 may decrease linearly (proportionally) from the inner diameter side to the outer diameter side, but may change linearly (proportionally) instead of linearly (proportional). .. Further, both the dimension a5 and the dimension H5 may become smaller from the inner diameter side to the outer diameter side of the resin thrust washer 20A. However, either the dimension a5 or the dimension H5 may become smaller from the inner diameter side to the outer diameter side of the resin thrust washer 20A.

(3) Third Configuration Example of Resin Thrust Washer 20A Next, the resin thrust washer 20A according to the third configuration example will be described. FIG. 14 is a plan view showing the configuration of the resin thrust washer 20A according to the third configuration example. FIG. 15 is a partial plan view showing the configuration of the resin thrust washer 20A according to the second configuration example. FIG. 16 is a cross-sectional view showing a state in which the oil groove 25 shown in FIGS. 14 and 15 is cut along the width direction.

In the resin thrust washer 20A according to the third configuration example shown in FIGS. 14 and 15, the oil groove 25 is a non-communication oil groove like the oil groove 25 of the resin thrust washer 20A according to the second configuration example. It is composed of 25a and is not provided with a communication oil groove 25b. However, in the third configuration example, the oil groove 25 may adopt a configuration in which the communicating oil groove 25b is provided together with the non-communication oil groove 25a. Further, as shown in FIGS. 15 and 16, the oil groove 25 has a bottom portion 251 and a tapered wall surface 252.

Here, as shown in FIGS. 15 and 16, in the resin thrust washer 20A according to the third configuration example, the dynamic pressure guide wall surface 254 is provided so as to be adjacent to the oil groove 25. The dynamic pressure guide wall surface 254 is a portion for easily guiding the lubricating oil that has entered the non-communication oil groove 25a to the sliding surface 26. Therefore, the inclination angle θ3 (see FIG. 16) of the dynamic pressure guide wall surface 254 with respect to the sliding surface 26 is provided to be significantly smaller than the inclination angle of the tapered wall surface 252 with respect to the sliding surface 26. By guiding the lubricating oil toward the sliding surface 26 on the dynamic pressure guide wall surface 254, pressure (dynamic pressure) due to the lubricating oil can be generated between the sliding surface 26 and other members. The pressure (dynamic pressure) makes it possible to reduce the sliding load with other members.

[4. Specific configuration of resin thrust washer 20B]
Next, the configuration of a resin thrust washer 20B (having a first oil groove 25c and a second oil groove 25d) having an oil groove 25 in a substantially V-shaped shape will be described below. The oil groove 25 provided in the resin thrust washer 20B is a non-communication oil groove 25a except for the communication oil groove 113 provided in the resin thrust washer 20 (see FIG. 27) according to the ninth configuration example described later. .. However, the resin thrust washer 20B may be provided with the communication oil groove 25b in a configuration other than the ninth configuration example.

(1) Fourth Configuration Example of Resin Thrust Washer 20B FIG. 17 is a partial plan view showing the configuration of the resin thrust washer 20B according to the fourth configuration example. As shown in FIGS. 3 and 17, the resin thrust washer 20B has a ring-shaped portion 21, an insertion hole 22, an oil introduction groove 23, a sliding surface 26, and an opening 27, similarly to the resin thrust washer 20A described above. And an oil barrier 28. However, in the resin thrust washer 20B, the form of the oil groove 25 is different. Specifically, in the resin thrust washer 20B, two oil grooves 25 having different inclination angles are connected on the opening 27 side, and these two oil grooves 25 are arranged so as to draw a V shape.

In the following description, one of the oil grooves 25 having a substantially V shape is referred to as a first oil groove 25c, and the other is referred to as a second oil groove 25d. In FIGS. 3 and 17, the first oil groove 25c is provided so as to proceed clockwise from the inner diameter side to the outer diameter side thereof. On the other hand, the second oil groove 25d is provided so as to proceed counterclockwise from the inner diameter side to the outer diameter side. When it is not necessary to distinguish between the first oil groove 25c and the second oil groove 25d, it is simply referred to as the oil groove 25.

Here, the first oil groove 25c and the second oil groove 25d may be completely connected on the opening 27 side, but they may be slightly separated from each other.

Further, as shown in FIG. 17, the inclination angle θ1 is preferably in the range of 30 degrees to 55 degrees also in the first oil groove 25c and the second oil groove 25d. The groove width of the oil groove 25 is preferably in the range of 1.8 mm to 2.8 mm. Further, the groove depth of the oil groove 25 is preferably in the range of 0.5 mm to 1.0 mm. In FIG. 17, the inclination angle θ1 on the first oil groove 25c side and the inclination angle θ1 on the second oil groove 25d side may be different values.

Further, the cross-sectional shape of the oil groove 25 according to the fourth configuration example shown in FIGS. 3 and 17 is formed as shown in FIG. In the configuration shown in FIG. 18, a pair of substantially S-shaped curved wall surfaces 255 are provided so as to face the sliding surface 26 side from the bottom portion 251 of the oil groove 25. Therefore, in any of the pair of curved wall surfaces 255, the lubricating oil that has entered the inside of the oil groove 25 can be satisfactorily supplied to the sliding surface 26.

Further, as shown in FIG. 18, the curved wall surface 255 on the other side (X2 side in FIG. 18) is provided with the dynamic pressure guide wall surface 254 so as to be continuous. The dynamic pressure guide wall surface 254 is a portion that is linearly inclined with a predetermined inclination angle with respect to the sliding surface 26. The dynamic pressure guide wall surface 254 may have a curved portion other than the linear portion.

Here, in the fourth configuration example, a total of 12 sets of the first oil groove 25c and the second oil groove 25d that draw a V shape are provided. In the sixth configuration example, the seventh configuration example, the eighth configuration example, and the eleventh configuration example, which will be described later, the first oil groove 25c and the second oil groove 25d drawing a V shape are similarly formed in the fourth configuration example. A total of 6 sets are provided. However, any number of sets of the first oil groove 25c and the second oil groove 25d that draw a V shape may be provided.

Here, in FIG. 17, the alternate long and short dash line shows the case where the rotation direction of the resin thrust washer 20B is clockwise, and also shows the flow of the lubricating oil at that time. When the resin thrust washer 20B rotates clockwise with respect to the lubricating oil existing on the insertion hole 22 side, the lubricating oil flowing into the oil groove 25 from the opening 27 is the first oil due to the action of centrifugal force. It is mainly supplied from the second oil groove 25d to the sliding surface 26 instead of the groove 25c. Further, in FIG. 17, the broken line shows the case where the rotation direction of the resin thrust washer 20 is counterclockwise, and also shows the flow of the lubricating oil at that time. When the resin thrust washer 20 rotates counterclockwise, the lubricating oil is mainly supplied from the first oil groove 25c to the sliding surface 26 instead of the second oil groove 25d due to the centrifugal force acting on the lubricating oil.

(2) Fifth Configuration Example of Resin Thrust Washer 20B Next, the resin thrust washer 20B according to the fifth configuration example will be described. FIG. 19 is a partial plan view showing the configuration of the resin thrust washer 20B according to the fifth configuration example. FIG. 20 is a cross-sectional view showing a state in which the oil groove 25 shown in FIG. 19 is cut along the width direction. The oil groove 25 of the resin thrust washer 20B according to the fifth configuration example has a cross-sectional shape along the width direction different from that of the oil groove 25 of the resin thrust washer 20B according to the fourth configuration example, but has the fifth configuration. In the resin thrust washer 20B according to the example, the configuration other than the cross-sectional shape of the oil groove 25 is common to the resin thrust washer 20B according to the fourth configuration example.

In the oil groove 25 according to the fifth configuration example shown in FIGS. 19 and 20, the tapered wall surface 252 is approached from the bottom portion 251 of the oil groove 25 toward one side (X1 side in FIG. 20). That is, the tapered wall surface 252 is continuous on one side of the bottom portion 251. On the other hand, when the bottom portion 251 is directed toward the other side (X2 side in FIG. 20), the curved wall surface 255 is approached in the same manner as the oil groove 25 shown in FIG. 18 described above. That is, the curved wall surface 255 is continuous on the other side of the bottom portion 251. The length of the tapered wall surface 252 in the width direction (dimension c12) is set so as to be approximately four times as large as the dimension a12 which is the length of the bottom portion 251 in the width direction.

Here, in the configuration in which the two oil grooves 25 are arranged so as to draw a V shape, as shown in FIG. 19, the tapered wall surface 252 is located on the inner diameter side of the curved wall surface 255 in the width direction of the oil grooves 25. It is provided as follows. As a result, when the resin thrust washer 20B is rotated, the lubricating oil is supplied to the sliding surface 26 of the portion not surrounded by the two oil grooves 25. However, the tapered wall surface 252 may be provided so as to be located on the outer diameter side of the curved wall surface 255 in the width direction of the oil groove 25.

In the fifth configuration example, a total of six sets of the first oil groove 25c and the second oil groove 25d forming a V shape are provided at equal intervals in the circumferential direction of the ring-shaped portion 21. However, any number of sets of the first oil groove 25c and the second oil groove 25d that draw a V shape may be provided.

(3) Sixth Configuration Example of Resin Thrust Washer 20B Next, the resin thrust washer 20B according to the sixth configuration example will be described. FIG. 21 is a partial plan view showing the configuration of the resin thrust washer 20B according to the sixth configuration example. FIG. 22 is a cross-sectional view showing a state in which the oil groove 25 shown in FIG. 21 is cut along the width direction. The plane shape of the oil groove 25 according to the sixth configuration example is different from that of the oil groove 25 according to the fourth configuration example, but the resin thrust washer 20B according to the sixth configuration example has a cross-sectional shape of the oil groove 25. Is common to the resin thrust washer 20B according to the fourth configuration example. That is, in the oil groove 25 according to the sixth configuration example, similarly to the oil groove 25 according to the fourth configuration example, the bottom portion 251 and the substantially S-shaped curvature are curved so as to face the sliding surface 26 side from the bottom portion 251. A pair of wall surfaces 255 are provided. Further, also in the oil groove 25 according to the sixth configuration example, the curved wall surface 255 on the other side (X2 side in FIG. 22) is provided with a linearly inclined dynamic pressure guide wall surface 254 so as to be continuous.

As shown in FIG. 21, the oil groove 25 is provided with a branch oil groove 110 in addition to the first oil groove 25c and the second oil groove 25d which are connected in a V shape. The branch oil groove 110 is an oil groove connected so as to branch from each of the first oil groove 25c and the second oil groove 25d. In the configuration shown in FIG. 21, the branch oil groove 110 is connected to the first oil groove 25c and the second oil groove 25d, respectively, so as to draw a lowercase letter “y” or vice versa. The outer diameter side of the branch oil groove 110 does not communicate with the outer peripheral side of the resin thrust washer 20B (ring-shaped portion 21), and the oil stops on the outer diameter side of the branch oil groove 110 like the oil groove 25. A wall 110a is arranged.

Further, in the configuration shown in FIG. 21, the branch oil groove 110 connected to the first oil groove 25c and the branch oil groove 110 connected to the second oil groove 25d are provided with the same width. However, the widths of the two branch oil grooves 110 may be different from each other. For example, the branch oil groove 110 connected to the first oil groove 25c may be provided wider than the branch oil groove 110 connected to the second oil groove 25d, and vice versa. It may have been done. Further, on the outer diameter side of the branch oil groove 110, an oil stop wall 110a for suppressing the lubricating oil from flowing out from the branch oil groove 110 from the outer peripheral side is provided. The width of the oil stop wall 110a can be set in the same manner as the width of the oil stop wall 28 described above.

(4) Seventh Configuration Example of Resin Thrust Washer 20B Next, the resin thrust washer 20B according to the seventh configuration example will be described. FIG. 23 is a partial plan view showing the configuration of the resin thrust washer 20B according to the seventh configuration example. FIG. 24 is a cross-sectional view showing a state in which the oil groove 25 shown in FIG. 23 is cut along the width direction. The plane shape of the oil groove 25 according to the seventh configuration example is different from that of the oil groove 25 according to the fourth configuration example, but the resin thrust washer 20B according to the seventh configuration example has a cross-sectional shape of the oil groove 25. The configuration excluding the vicinity is the same as that of the resin thrust washer 20B according to the fourth configuration example.

Specifically, as shown in FIG. 24, the tapered wall surface 252 is approached from the bottom 251 of the oil groove 25 toward one side (X1 side in FIG. 24). That is, the tapered wall surface 252 is continuous on one side of the bottom portion 251. On the other hand, from the bottom portion 251 toward the other side (X2 side in FIG. 24), the oil embankment portion 109 reaches the inclined wall portion 109a. That is, the inclined wall portion 109a is continuous on the other side of the bottom portion 251. Here, in the configuration shown in FIG. 24, the dimension is set so that the length (dimension c14) of the tapered wall surface 252 in the width direction is substantially double the dimension a14 which is the length of the bottom portion 251 in the width direction. Has been done.

Further, the oil bank portion 109 is provided so that the height H141 from the bottom portion 251 is about the same as the height H142 of the sliding surface 26 from the bottom portion 251. The oil bank portion 109 is provided with a pair of inclined wall portions 109a and 109b with a top portion 109c interposed therebetween. As described above, the inclined wall portion 109a is an inclined wall located on the other side (X2 side) of the oil groove 25, and is inclined linearly. Further, the inclined wall portion 109b is an inclined wall located on the opposite side of the inclined wall portion 109a with the top portion 109c interposed therebetween, and is inclined linearly like the inclined wall portion 109a. As shown in FIG. 24, the inclined wall portion 109a is arranged on one side (X1 side) of the top portion 109c, and the inclined wall portion 109b is arranged on the other side (X2 side) of the top portion 109c. The inclined wall portions 109a and 109b are not limited to a straight line, but may be provided in a curved shape.

The bottom portion 251 side of the inclined wall portion 109a and the surrounding portion 111 (described later) side of the inclined wall portion 109b are provided in a straight line. However, the tops 109c side of the inclined wall portions 109a and 109b are provided in a curved shape.

Further, the top 109c is provided so as to be flat, but the width of the top 109c is very narrow as compared with the width of the bottom 251 and the tapered wall surface 252. As described above, since the width of the top 109c is very narrow, even when the top 109c comes into contact with other members (other resin thrust washers 20, metal thrust washers, mating materials C1, C2, etc.), It is provided so as to make contact in a line contact manner. More specifically, as shown in FIGS. 23 and 24, the first oil groove 25c and the second oil groove 25d are surrounded by these two oil grooves 25 (two oil stop walls 28). The surrounding portion 111 is provided. As shown in FIG. 24, the height of the surrounding portion 111 is set lower than the height of the top portion 109c. Therefore, when the resin thrust washer 20 is rotated, the surrounding portion 111 does not come into contact with other members even if the top portion 109c may come into contact with other members.

When the resin thrust washer 20 is rotated, the lubricating oil that has passed over the top 109c covers the surrounding portion 111. Even if the lubricating oil covers the surrounding portion 111, the surrounding portion 111 is in a state of not coming into contact with other members.

In this way, when the resin thrust washer 20 is rotated, the surrounding portion 111 having a low height does not come into contact with other members, while the top 109c may come into contact with other members. It is possible to reduce the sliding load as compared with the configuration in which 111 does not exist. The height of the surrounding portion 111 may be about the same as that of the bottom portion 251 and may be slightly higher or lower than that of the bottom portion 251. Further, when the resin thrust washer 20 is rotated, the top 109c may come into contact with other members, but it goes without saying that the top 109c may not come into contact with other members due to the presence of lubricating oil. ..

(5) Eighth Configuration Example of Resin Thrust Washer 20B Next, the resin thrust washer 20B according to the eighth configuration example will be described. FIG. 25 is a partial plan view showing the configuration of the resin thrust washer 20B according to the eighth configuration example. FIG. 26 is a cross-sectional view showing a state in which the oil groove 25 shown in FIG. 25 is cut along the width direction. The plane shape of the oil groove 25 according to the eighth configuration example is different from that of the oil groove 25 according to the fourth configuration example, but in the resin thrust washer 20B according to the eighth configuration example, the oil groove 25 is the first. Like the four configuration examples, it has a bottom portion 251. Hereinafter, the difference between the resin thrust washer 20B according to the eighth configuration example and the resin thrust washer 20B according to the fourth configuration example to the seventh configuration example will be described.

As shown in FIG. 26, the resin thrust washer 20B according to the eighth configuration example is provided with a convex curved surface portion 256 similar to a substantially S-shaped curved wall surface 255. The convex curved surface portion 256 is a convex curved surface connecting the bottom portion 251 and the sliding surface 26, but unlike the substantially S-shaped curved wall surface 255, it has a cross-sectional shape in which no inflection point exists. In the configuration shown in FIG. 26, the convex curved surface portion 256 is provided in a shape equivalent to, for example, a round chamfer. However, in the convex curved surface portion 256, for example, a linear portion may be partially present or a concave curved surface portion may be partially present in addition to the convex curved surface portion. Further, instead of the convex curved surface portion 256, a linear inclined surface equivalent to the tapered wall surface 252 may be provided.

In the configuration shown in FIG. 25, the oil groove 25 has a wide groove portion 257 and a narrow groove portion 258. The wide groove portion 257 and the narrow groove portion 258 are provided so as to be continuous on the same straight line. As shown in FIG. 25, the wide groove portion 257 is provided so as to be wider than the narrow groove portion 258. Further, while the narrow groove portion 258 is connected to the opening 27, an oil stop wall 28 exists on the back side of the wide groove portion 257. In the configuration shown in FIG. 25, the width of the wide groove portion 257 is set so as to be approximately 2 to 2.5 times the width of the narrow groove portion 258.

(6) About the Ninth Configuration Example of the Resin Thrust Washer 20B Next, the resin thrust washer 20A according to the ninth configuration example will be described. FIG. 27 is a partial plan view showing the configuration of the resin thrust washer 20B according to the ninth configuration example. FIG. 28 is a cross-sectional view showing a state in which the oil groove 25 shown in FIG. 27 is cut along the width direction. In the resin thrust washer 20A according to the ninth configuration example, the oil groove 25 is different from the resin thrust washer 20B according to the fourth configuration example to the eighth configuration example, and the two oil grooves 25 draw a V shape. The oil groove 25 is arranged so as to extend in a direction in which it is inclined with respect to the radial direction. However, also in the resin thrust washer 20A according to the ninth configuration example, the two oil grooves 25 may be arranged so as to draw a V shape.

The oil groove 25 according to the ninth configuration example includes a bottom portion 251 and a dynamic pressure guide wall surface 254, similarly to the oil groove 25 according to the fourth configuration example. Further, the oil groove 25 according to the ninth configuration example includes a convex curved surface portion 256, similarly to the oil groove 25 according to the eighth configuration example. However, the resin thrust washer 20B according to the ninth configuration example is provided with a sliding protrusion 112 similar to the oil bank portion 109 from the bottom portion 251 toward the other side (X2 side in FIGS. 27 and 28). There is. The sliding protrusion 112 is a portion that comes into contact with the mating material C1 or C2 to smooth the roughness on the surface of the mating material C1 or C2. Therefore, the sliding protrusion 112 is provided at the same height as the sliding surface 26 or slightly protruding from the sliding surface 26. Instead of the convex curved surface portion 256, a linear inclined surface equivalent to the tapered wall surface 252 may be provided. Further, the sliding protrusion 112 may be provided slightly lower than the sliding surface 26.

As shown in FIGS. 27 and 28, when the bottom portion 251 is directed toward the other side (X2 side in FIGS. 27 and 28), the sliding protrusion 112 approaches the inclined wall portion 112a. That is, the inclined wall portion 112a is continuous on the other side of the bottom portion 251. Further, the inclined wall portion 112a is continuous with the top surface portion 112b of the sliding protrusion 112. The top surface portion 112b is provided so as to be flat like the top portion 109c. Further, the concave curved surface portion 113b, which will be described later, is continuous with the top surface portion 112b.

Further, in the resin thrust washer 20A according to the ninth configuration example, the communication oil groove 113 (corresponding to the adjacent communication oil groove) is provided from the sliding protrusion 112 toward the other side (X2 side in FIGS. 27 and 28). It is provided. In the communicating oil groove 113, the oil stop wall 28 does not exist on the outer diameter side of the ring-shaped portion 21, and the lubricating oil can flow freely from the insertion hole 22 to the outer diameter side. In the configurations shown in FIGS. 27 and 28, the communicating oil groove 113 is provided so as to be recessed from the sliding surface 26 together with the oil groove 25. Further, in the configurations shown in FIGS. 27 and 28, the communication oil groove 113 is provided in a straight line so as to be parallel to the oil groove 25. However, the communication oil groove 113 does not have to be parallel to the oil groove 25, and may be provided along the radial direction of the resin thrust washer 20A, for example. Further, the communication oil groove 113 may be provided in a curved shape instead of a straight line.

The bottom 113a of the communication oil groove 113 is provided at the same height as the bottom 251. However, the height of the bottom 113a may have a slight height difference with respect to the height of the bottom 251. .. Further, as shown in FIG. 28, the bottom portion 113a is continuously provided on the pair of concave curved surface portions 113b and 113c. Of these, a concave curved surface portion 113b is provided on one side of the bottom portion 113a (X1 side in FIG. 28), and a concave curved surface portion 113c is provided on the other side of the bottom portion 113a (X2 side in FIG. 28). ing. These concave curved surface portions 113b and 113c are concave curved surfaces connecting the bottom portion 113a and the sliding surface 26, and unlike the substantially S-shaped curved wall surface 255, have a cross-sectional shape in which no inflection point exists. In the configuration shown in FIG. 28, the concave curved surface portions 113b and 113c are provided in the same shape as, for example, round chamfered. However, the concave curved surface portions 113b and 113c may have, for example, a linear portion in addition to the curved surface-shaped portion. Further, the bottom 113a may or may not have a curved surface portion.

When such a communication oil groove 113 is provided, it is possible to increase the flow rate of the lubricating oil passing through the communication oil groove 113 toward the outer diameter side. Therefore, it is possible to improve the heat dissipation of the resin thrust washer 20A.

(7) About 10th Configuration Example of Resin Thrust Washer 20B Next, the resin thrust washer 20B according to the 10th configuration example will be described. The resin thrust washer 20B according to the tenth configuration example is provided with an oil groove 25 similar to the resin thrust washer 20B according to the fifth configuration example described above, and the similar oil groove 25 has a bottom portion 251 and an oil groove 25. There are a substantially S-shaped curved wall surface 255 and a tapered wall surface 252. Therefore, the illustration is omitted. However, in the tenth configuration example, a total of eight sets of the first oil groove 25c and the second oil groove 25d forming a V shape are provided at equal intervals in the circumferential direction of the ring-shaped portion 21. In this respect, a total of six sets of the first oil groove 25c and the second oil groove 25d are different from the fifth configuration example provided in the ring-shaped portion 21.

(8) Eleventh Configuration Example of Resin Thrust Washer 20B Next, the resin thrust washer 20B according to the eleventh configuration example will be described. FIG. 29 is a partial plan view showing the configuration of the resin thrust washer 20B according to the eleventh configuration example. FIG. 30 is a cross-sectional view showing a state in which the oil groove 25 shown in FIG. 29 is cut along the width direction.

In the resin thrust washer 20B according to the eleventh configuration example, the first oil groove 25c and the second oil groove 25d are provided with short lengths. Therefore, there is a sufficient distance between the inner peripheral side of the first oil groove 25c and the second oil groove 25d (the side away from the opening 27) and the outer peripheral edge portion of the resin thrust washer 20B.

Further, the resin thrust washer 20B according to the eleventh configuration example is provided with an oil sump groove 114 in addition to the oil groove 25. The oil sump groove 114 is a concave portion in which the opening 27 does not exist on the inner diameter side thereof. In the configuration shown in FIG. 29, two oil sump grooves 114 are provided. These two oil reservoirs 114 are connected on the inner diameter side so as to draw a V shape. However, the oil sump groove 114 does not have to be arranged so as to draw a V shape. In the following description, one of the V-shaped oil sump grooves 114 will be referred to as a first oil sump groove 114a, and the other other will be referred to as a second oil sump groove 114b. The first oil sump groove 114a is provided so as to advance clockwise from the inner diameter side to the outer diameter side thereof. On the other hand, the second oil sump groove 114b is provided so as to proceed counterclockwise from the inner diameter side to the outer diameter side thereof.

Further, in the eleventh configuration example, the cross-sectional shape of the oil groove 25 and the oil sump groove 114 is a substantially S-shaped curved wall surface 255 from the bottom 251 of the oil groove 25 toward one side (X1 side in FIG. 30). Is approaching. That is, a substantially S-shaped curved wall surface 255 is continuous on one side of the bottom portion 251. In this curved wall surface 255, a concave curved surface portion 259 which is a concave curved surface is continuously provided on the bottom portion 251, and a convex curved surface portion 256 which is a convex curved surface is continuously provided with respect to the concave curved surface portion 259. It is provided. Further, a dynamic pressure guide wall surface 254 is provided between the convex curved surface portion 256 and the sliding surface 26 so as to be continuous with the convex curved surface portion 256. Instead of the convex curved surface portion 256, a linear inclined surface equivalent to the tapered wall surface 252 may be provided.

On the other hand, from the bottom portion 251 toward the other side (X2 side in FIG. 30), the concave curved surface portion 260 is continuously provided on the bottom portion 251. Further, the concave curved surface portion 260 is continuously provided with an inclined wall portion 261 that is inclined in a straight line. The sliding surface 26 is approached from the inclined wall portion 261 toward the other side (X2 side in FIG. 30). Further, the inclined wall portion 261 may be provided in a curved surface shape. Further, the inclined wall portion 261 may have a curved surface portion.

Further, similarly to the oil groove 25 described above, when the oil pool groove 114 is directed from the bottom 115 (see FIG. 29) to one side in the width direction, the concave curved surface portion (not shown) and the convex curved surface similar to the concave curved surface portion 259 It approaches the sliding surface 26 through a convex curved surface portion (not shown) similar to the portion 256 and a dynamic pressure guide wall surface 116 (see FIG. 29) similar to the dynamic pressure guide wall surface 254. Further, when the bottom portion 115 is directed to the other side in the width direction, the sliding surface 26 passes through a concave curved surface portion (not shown) similar to the concave curved surface portion 260 and an inclined wall portion (not shown) similar to the inclined wall portion 261. Is approaching. Instead of the convex curved surface portion 256, a linear inclined surface equivalent to the tapered wall surface 252 may be provided.

Here, the height from the bottom 251 to the sliding surface 26 (groove depth of the oil groove 25) H1 to H6, H11 to H13, H15, H16, H18, H141, H142, and the dimensions of the oil scooping surface 24. The relationship is as shown in FIG. That is, the height T from the inner peripheral end of the oil scooping surface 24 to the sliding surface 26 is larger than the height from the bottom 251 to the sliding surface 26 (hereinafter referred to as the height Hx). It is provided as follows.

In particular, the lubricating oil moves in the circumferential direction along the oil scooping surface 24 when the thrust washer 10 rotates, and flows into the oil groove 25 from each opening 27. Therefore, if the height T is not sufficiently large with respect to the height Hx, the amount of lubricating oil flowing into the oil groove 25 from the opening 27 may decrease. Therefore, it is preferable that the height T is provided in a dimension that is twice or more the height Hx. Further, the inclination angle α of the oil scooping surface 24 with respect to the axial direction of the thrust washer 10 is preferably in the range of 30 to 60 degrees. Here, when the inclination angle α is smaller than 30 degrees, the radial dimension of the oil scooping surface 24 becomes small, and the supply amount of the lubricating oil decreases. On the other hand, when the inclination angle α is larger than 60 degrees, the oil scooping surface 24 occupies the radial direction in order to realize a state in which the height T is twice or more the height Hx as described above. The ratio will increase. Further, when the radial dimension of the oil scooping surface 24 is fixed, the height Hx becomes low (small). Therefore, the inclination angle α is preferably within the above range. In the range of the above-mentioned suitable inclination angle α of 30 to 60 degrees, 45 degrees in the center of the range is a typical example, but the inclination angle α is appropriately specified from the above-mentioned range of 30 to 60 degrees. Can be selected. The inclination angle α may be outside the range of 30 to 60 degrees.

Further, the inclination angle β (not shown) formed by the groove bottom of the oil introduction groove 23 with respect to the axial direction is provided to be smaller than the inclination angle α of the oil scooping surface 24 as described above. Specifically, the inclination angle β is provided to be smaller than the inclination angle α while including 0 degrees (may be 0 degrees). As a result, a relatively large step is provided on the boundary wall between the oil introduction groove 23 and the oil scooping surface 24 (see FIG. 12 and others). Therefore, when the lubricating oil enters the oil introduction groove 23, the lubricating oil can be satisfactorily supplied to the oil scooping surface 24 side. When the inclination angle β is 0 degree, the groove bottom portion of the oil introduction groove 23 is in a state parallel to the axial direction.

Further, it is preferable that at least a part of the boundary wall with the oil scooping surface 24 of the oil introduction groove 23 is slightly inclined with respect to the radial direction of the thrust washer 10 (ring-shaped portion 21). As an example of such a slightly inclined portion on the boundary wall, for example, a configuration in which the base portion with the bottom portion of the oil introduction groove 23 located outside in the radial direction of the oil introduction groove 23 is R-shaped can be mentioned. Be done. In addition to the R shape, a boundary wall may be provided so that the dimension in the circumferential direction becomes smaller than the inside of the oil introduction groove 23 toward the outside in the radial direction.

[5. Evaluation of the shape of the oil groove 25 of the resin thrust washers 20A and 20B (experimental results)]
Next, regarding the resin thrust washers 20A and 20B, the evaluation (experimental result) regarding the shape of the oil groove 25 will be described below.

(1) Experimental conditions and load measuring device 300 First, the experimental conditions will be described. The resin thrust washer 20A in which the experiment was conducted has an outer diameter of 67 mm, an inner diameter of 49 mm, and a thickness of 1 mm. Further, the resin thrust washer 20A according to the first configuration example and the second configuration example is provided with an oil groove 25 on one side thereof, and the resin thrust washer 20A according to the third configuration example has an oil groove 25 on both sides thereof. An oil groove 25 is provided. The resin thrust washer 20A is manufactured by using the trade name 150FC30 (manufactured by Victrex) made of polyetherketone resin (PEK). Further, the resin thrust washer 20 is not surface-treated. Further, the mating materials C1 and C2 arranged to face the resin thrust washer 20A use high-strength steel S45C (JIS standard), the diameter thereof is 67 mm, and the surface roughness thereof is Rz 0.5 μm. .. Further, in this experiment, both sides of the resin thrust washer 20A are slid, and the mating materials C1 and C2 slid on both sides have a Vickers hardness (HV) of 180. Further, ATF is used as the oil type of the lubricating oil, and the oil temperature at the time of conducting the experiment is 120 degrees. At the time of the experiment, the load was 1135 N, the rotation speed was 6800 rpm, and the oil flow rate was 100 cc / min.

Further, in the resin thrust washer 20A described above, the sliding load was measured by using the load measuring device 300 as shown in FIG. 32. The load measuring device 300 includes a cylindrical oil pan 301, and the above-mentioned lubricating oil is supplied to the inner cylinder portion 301a of the oil pan 301. The oil pan 301 is also provided with an oil discharge port 301b. The oil discharge port 301b is an opening portion for discharging the lubricating oil existing in the inner cylinder portion 301a to the outside, and has a mechanism for forcibly discharging the lubricating oil by a pump.

Further, the load measuring device 300 includes a fixed shaft 302 and a rotating shaft 303. The fixed shaft 302 is a shaft that does not rotate relative to the oil pan 301. However, a load in the pressing direction is applied to the fixed shaft 302 from a load supply means (not shown). Further, the mating material C2 is attached to the fixed shaft 302 in a non-rotating state with respect to the fixed shaft 302.

Further, the rotation shaft 303 is a shaft that rotates with respect to the oil pan 301. Therefore, the rotating shaft 303 is provided with a driving force that rotates from the rotational force supply means (not shown). Further, the mating material C1 is attached to the rotating shaft 303 in a non-rotating state with respect to the rotating shaft 303. The mating material C1 is provided with a shaft-shaped portion C1a for attaching the resin thrust washer 20A. On the other hand, the other mating material C2 is provided in a disk shape. Therefore, the axial dimension of one mating material C1 is larger than that of the other mating material C2 by the presence of the shaft-shaped portion C1a.

As shown in FIG. 32, a central hole is provided so as to penetrate each of the fixed shaft 302, the mating material C1 and the other mating material C2 (reference numerals are omitted). Then, when these central holes are continuous in the axial direction, an oil supply path 304 through which the lubricating oil flows is formed. The fixed shaft 302 is formed with an oil supply port 302a, which is an opening portion for supplying lubricating oil to the oil supply path 304. Further, a thermocouple 305 is attached to the mating material C2. The thermocouple 305 is a portion for measuring the sliding surface temperature of the mating material C2. In the oil pan 301, an oil seal 306 is provided at an opening portion (reference numeral omitted) for inserting the fixed shaft 302 into the inner cylinder portion 301a. Further, in the oil pan 301, an oil seal 307 is also provided at an opening portion for inserting the rotating shaft 303 into the inner cylinder portion 301a.

(2) Experimental Results of Sliding Area Ratio (Oil Groove Area Ratio) of Resin Thrust Washer 20A According to First Configuration Example The resin thrust washer 20A according to the first configuration example is attached to the above load measuring device 300. FIG. 33 shows the results of an experiment on the relationship between the sliding area ratio and the torque (average torque) of the resin thrust washer 20A. In the experiment shown in FIG. 33, an experiment was conducted on a resin thrust washer 20A according to the first configuration example, which has a non-communication oil groove 25a and a communication oil groove 25b as shown in FIG. The dimension corresponding to the width of the bottom portion 251 is 2.00 mm, the dimension corresponding to the width of the oil groove 25 is 3.50 mm, and the height from the bottom portion 251 to the sliding surface 26 is 0.30 mm. Then, in this experiment, the sliding area ratio is changed by changing the number of oil grooves 25 and the groove width, and the experiment is conducted. Of the points shown in FIG. 33, the point where the sliding area ratio is 100% (oil groove area ratio is 0%) corresponds to Comparative Example 1, and the sliding area ratio is 90% (oil groove area ratio is 0%). The point of 10%) corresponds to Comparative Example 2, the point of sliding area ratio of 85% (oil groove area ratio is 15%) corresponds to Example 1, and the sliding area ratio is 80% (oil groove area). The point of 20%) corresponds to Example 2, the point of sliding area ratio of 70% (oil groove area ratio is 30%) corresponds to Example 3, and the sliding area ratio is 60% (oil). The point of (groove area ratio of 40%) corresponds to Example 4, and the point of sliding area ratio of 50% (oil groove area ratio is 50%) corresponds to Comparative Example 3.

Table 1 shows the torque (sliding load), the amount of wear, and their determination results (torque determination and wear amount determination) corresponding to the experimental results of FIG. 33. In the torque determination in Table 1, the resin thrust washer 20A having a torque (sliding load) of 0.7 Nm or less is indicated by "A" as satisfying the criteria for low sliding load, and the torque (sliding load) is indicated. ) Is larger than 0.7 Nm, and the resin thrust washer 20A is indicated by "B" as not satisfying the standard of low sliding load. Further, in the wear amount determination in Table 1, the resin thrust washer 20A having a wear amount of 20 μm or less is indicated by “A” as satisfying the criteria for low wear amount, and the resin thrust washer 20A having a wear amount larger than 20 μm is indicated by “A”. Is indicated by "B" as not satisfying the criteria of low and low wear amount.

In the experiments shown in FIGS. 33 and 1, the results of sliding each resin thrust washer 20A for 5 hours are shown.

From such experimental results, if the sliding area ratio is in the range of 60% to 85% (that is, the oil groove area ratio is in the range of 15% to 40%), the average torque is 0.7 Nm or less. It can be said that it is preferable because it becomes smaller. Further, if the sliding area ratio is in the range of 60% to 85% (that is, the oil groove area ratio is in the range of 15% to 40%), the amount of wear is as small as 20 μm or less, which is preferable. I can say.

In Comparative Examples 1 and 2, it is considered that the oil groove area ratio is too low and the lubricity of the lubricating oil is deteriorated.

(3) Experimental Results of Sliding Area Ratio (Oil Groove Area Ratio) of Resin Thrust Washer 20A According to Second Configuration Example Next, the load measuring device 300 described above is as shown in FIGS. 11 and 12. FIG. 34 shows the experimental results regarding the relationship between the sliding area ratio and the torque (average torque) of the resin thrust washer 20A, which was carried out by attaching the resin thrust washer 20A according to the second configuration example. In this experiment, the dimension corresponding to the width of the bottom 251 is 0.80 mm, the dimension corresponding to the width of the oil groove 25 is 2.10 mm, and the height from the bottom 251 to the sliding surface 26 is 0.30 mm. .. Then, in this experiment, the sliding area ratio is changed by changing the number of oil grooves 25 and the groove width, and the experiment is conducted. The experimental conditions are the same as the experimental results shown in FIG. 33 and Table 1.

Of the points shown in FIG. 34, the point where the sliding area ratio is 90% (oil groove area ratio is 10%) corresponds to Comparative Example 11, and the sliding area ratio is 85% (oil groove area ratio). The point of 15%) corresponds to Example 11, the point of sliding area ratio of 80% (oil groove area ratio is 20%) corresponds to Example 12, and the sliding area ratio is 70% (oil groove area). The point where the rate is 30% corresponds to Example 13, the point where the sliding area ratio is 60% (oil groove area ratio is 40%) corresponds to Example 14, and the sliding area ratio is 50% (oil). The point that the groove area ratio is 50%) corresponds to Comparative Example 12.

Table 2 shows the torque (sliding load), the amount of wear, and their determination results (torque determination and wear amount determination) corresponding to the experimental results of FIG. 34. In the torque determination in Table 2, the resin thrust washer 20A having a torque (sliding load) of 0.2 Nm or less is indicated by "A" as satisfying the criteria for low sliding load, and the torque (sliding load) is indicated. ) Is larger than 0.2 Nm, the resin thrust washer 20A is indicated by "B" as not satisfying the standard of low sliding load. Further, in the wear amount determination in Table 2, the resin thrust washer 20A having a wear amount of 30 μm or less is indicated by “A” as satisfying the criteria for low wear amount, and the resin thrust washer 20A having a wear amount larger than 30 μm is indicated by “A”. Is indicated by "B" as not satisfying the criteria of low and low wear amount.

From such experimental results, if the sliding area ratio is in the range of 60% to 85% (that is, the oil groove area ratio is in the range of 15% to 40%), the average torque is 0.2 Nm or less. It can be said that it is preferable because it becomes smaller. Further, within the range of the experiment, the amount of wear is as small as 20 μm or less in the entire range. From these results, in the resin thrust washer 20A according to the second configuration example, the sliding area ratio is in the range of 60% to 85% (that is, the oil groove area ratio is in the range of 15% to 40%). It can be said that it is preferable because it meets the criteria of both low sliding load and low wear amount.

In Comparative Example 11, since the shear resistance of the lubricating oil is large, it is considered that the torque (sliding load) is large. Further, in Comparative Example 12, since the oil groove area ratio is as large as 50%, it is considered that the torque (sliding load) is large because the contact surface is small and the surface pressure of the sliding surface 26 is high. To be done.

(4) Experimental Results of Sliding Area Ratio (Oil Groove Area Ratio) of Resin Thrust Washer 20B According to Fourth Configuration Example Next, the load measuring device 300 described above is as shown in FIGS. 17 and 18. An experiment was conducted with the resin thrust washer 20B according to the fourth configuration example attached. In this experiment, experimental results were obtained regarding the relationship between the sliding area ratio and the torque (average torque) of the resin thrust washer 20B. The experimental results are shown in FIG. In this experiment, the dimension corresponding to the width of the bottom 251 is 0.50 mm, the dimension corresponding to the width of the oil groove 25 is 1.50 mm, and the height from the bottom 251 to the sliding surface 26 is 0.25 mm. .. Then, in this experiment, the sliding area ratio is changed by changing the number of oil grooves 25 and the groove width, and the experiment is conducted. The experimental conditions are the same as the experimental results shown in FIGS. 18 and 1.

Of the points shown in FIG. 35, the point where the sliding area ratio is 90% (oil groove area ratio is 10%) corresponds to Comparative Example 21, and the sliding area ratio is 85% (oil groove area ratio). The point of 15%) corresponds to Example 21, the point of sliding area ratio of 80% (oil groove area ratio is 20%) corresponds to Example 22, and the sliding area ratio is 70% (oil groove area). The point where the rate is 30% corresponds to Example 23, the point where the sliding area ratio is 60% (oil groove area ratio is 40%) corresponds to Example 24, and the sliding area ratio is 50% (oil). The point that the groove area ratio is 50%) corresponds to Comparative Example 22.

Table 3 shows the torque (sliding load), the amount of wear, and their determination results (torque determination and wear amount determination) corresponding to the experimental results of FIG. 35. The judgment standard for torque judgment in Table 3 is "A" when it is 0.2 Nm or less, "B" when it is larger than 0.2 Nm, and the judgment standard for wear amount judgment is 30 μm or less. Is "A", and the case where it is larger than 30 μm is “B”, which are the same as in Table 2.

From such experimental results, if the sliding area ratio is in the range of 60% to 85% (that is, the oil groove area ratio is in the range of 15% to 40%), the average torque is 0.2 Nm or less. It can be said that it is preferable because it becomes smaller. Further, if the sliding area ratio is in the range of 50% to 85% (that is, the oil groove area ratio is in the range of 15% to 50%), the amount of wear is as small as 30 μm or less, which is preferable. I can say. From these results, in the resin thrust washer 20B according to the fourth configuration example, the sliding area ratio is in the range of 60% to 85% (that is, the oil groove area ratio is in the range of 15% to 40%). It can be said that it is preferable because it meets the criteria of both low sliding load and low wear amount.

In Comparative Example 21, since the shear resistance of the lubricating oil is large, it is considered that the torque (sliding load) is large. Further, in Comparative Example 22, since the oil groove area ratio is as large as 50%, it is considered that the torque (sliding load) is large because the contact surface is small and the surface pressure of the sliding surface 26 is high. To be done.

(5) Experimental results on the groove angle when the sliding area ratio is 85% (oil groove area ratio is 15%) in the resin thrust washer 20A according to the second configuration example. An experiment was conducted by attaching a resin thrust washer 20A according to the second configuration example as shown and having a sliding area ratio of 85% (oil groove area ratio of 15%) to the above-mentioned load measuring device 300. The experimental results are shown in Table 4. Table 4 shows the torque (sliding load), the amount of wear, and the determination results (torque determination and wear amount determination) when the groove angle is changed. In Table 4, the case where the groove angle of the oil groove 25 is 30 degrees corresponds to Example 31, and the case where the groove angle of the oil groove 25 is 40 degrees corresponds to Example 32, and the groove angle of the oil groove 25 corresponds to Example 32. 45 degrees corresponds to Example 33, the groove angle of the oil groove 25 corresponds to Example 34, and the groove angle of the oil groove 25 corresponds to Example 35. The case where the groove angle of the oil groove 25 is 60 degrees corresponds to the thirty-sixth embodiment.

The judgment standard for torque judgment in Table 4 is "A" when it is 0.2 Nm or less, and "B" when it is larger than 0.2 Nm, and the judgment standard for wear amount judgment is 30 μm or less. The case is “A”, and the case larger than 30 μm is “B”, which are the same as in Table 2.

From such experimental results, when the sliding area ratio is 85% (that is, the oil groove area ratio is 15%), the average torque is 0.2 N · in the groove angle of the oil groove 25 within the range of 30 to 60 degrees. It can be said that it is preferable because the amount of wear is as small as 30 μm or less as well as being as small as m or less.

(6) Regarding the experimental results regarding the groove angle when the sliding area ratio is 70% (oil groove area ratio is 30%) in the resin thrust washer 20A according to the second configuration example, FIG. 11 and FIG. 12 show. An experiment was conducted by attaching a resin thrust washer 20A having a sliding area ratio of 70% (oil groove area ratio of 30%) to the above-mentioned load measuring device 300 as shown in the second configuration example. The experimental results are shown in Table 5. Table 5 shows the torque (sliding load), the amount of wear, and the determination results (torque determination and wear amount determination) when the groove angle is changed. In Table 5, the case where the groove angle of the oil groove 25 is 30 degrees corresponds to the embodiment 41, the case where the groove angle of the oil groove 25 is 40 degrees corresponds to the embodiment 42, and the groove angle of the oil groove 25 corresponds to the embodiment 42. 45 degrees corresponds to Example 43, oil groove 25 corresponds to Example 44 when the groove angle is 50 degrees, and oil groove 25 corresponds to Example 45 when the groove angle is 55 degrees. The case where the groove angle of the oil groove 25 is 60 degrees corresponds to the 46th embodiment.

The judgment standard for torque judgment in Table 5 is "A" when it is 0.2 Nm or less, "B" when it is larger than 0.2 Nm, and the judgment standard for wear amount judgment is 30 μm or less. The case is “A”, and the case larger than 30 μm is “B”, which are the same as in Table 2.

From such experimental results, when the sliding area ratio is 70% (that is, the oil groove area ratio is 30%), the average torque is 0.2 N · in the groove angle of the oil groove 25 within the range of 30 degrees to 60 degrees. It can be said that it is preferable because the amount of wear is as small as 30 μm or less as well as being as small as m or less.

(7) Regarding the experimental results regarding the groove angle when the sliding area ratio is 60% (oil groove area ratio is 40%) in the resin thrust washer 20A according to the second configuration example, FIG. 11 and FIG. 12 show. An experiment was conducted by attaching a resin thrust washer 20A according to the second configuration example as shown and having a sliding area ratio of 60% (oil groove area ratio of 40%) to the above-mentioned load measuring device 300. The experimental results are shown in Table 6. Table 6 shows the torque (sliding load), the amount of wear, and the determination results (torque determination and wear amount determination) when the groove angle is changed. In Table 6, the case where the groove angle of the oil groove 25 is 30 degrees corresponds to the embodiment 51, the case where the groove angle of the oil groove 25 is 40 degrees corresponds to the embodiment 52, and the groove angle of the oil groove 25 corresponds to the embodiment 52. 45 degrees corresponds to Example 53, the groove angle of the oil groove 25 corresponds to Example 54, and the groove angle of the oil groove 25 corresponds to Example 55. The case where the groove angle of the oil groove 25 is 60 degrees corresponds to the 56th embodiment.

The judgment standard for torque judgment in Table 6 is "A" when it is 0.2 Nm or less, and "B" when it is larger than 0.2 Nm, and the judgment standard for wear amount judgment is 30 μm or less. The case is “A”, and the case larger than 30 μm is “B”, which are the same as in Table 2.

From such experimental results, when the sliding area ratio is 60% (that is, the oil groove area ratio is 40%), the average torque is 0.2 N · in the groove angle of the oil groove 25 within the range of 30 degrees to 60 degrees. It can be said that it is preferable because the amount of wear is as small as 30 μm or less as well as being as small as m or less.

(8) Experimental results on the groove angle when the sliding area ratio is 85% (oil groove area ratio is 15%) in the resin thrust washer 20A according to the fourth configuration example. An experiment was conducted by attaching a resin thrust washer 20B having a sliding area ratio of 85% (oil groove area ratio of 15%) to the above-mentioned load measuring device 300 as shown in the fourth configuration example. The experimental results are shown in Table 7. Table 7 shows the torque (sliding load), the amount of wear, and the determination results (torque determination and wear amount determination) when the groove angle is changed. In Table 7, the case where the groove angle of the oil groove 25 is 30 degrees corresponds to the embodiment 61, the case where the groove angle of the oil groove 25 is 40 degrees corresponds to the embodiment 62, and the groove angle of the oil groove 25 corresponds to the embodiment 62. 45 degrees corresponds to Example 63, the groove angle of the oil groove 25 corresponds to Example 64, and the groove angle of the oil groove 25 corresponds to Example 65. The case where the groove angle of the oil groove 25 is 60 degrees corresponds to Comparative Example 61.

The judgment criteria for torque judgment in Table 7 are "A" when the torque is 0.2 Nm or less, "B" when the torque is larger than 0.2 Nm, and "C" when the resin thrust washer 20A cannot be manufactured. The criteria for determining the amount of wear are "A" when the amount of wear is 30 μm or less, "B" when the amount is larger than 30 μm, and "C" when the resin thrust washer 20A cannot be manufactured. It is the same as the case of. In the torque determination and the wear amount determination in Table 7, there is no determination "B", and the determination "A" and the determination "C" exist.

In such an experimental result, when the sliding area ratio is 85% (that is, the oil groove area ratio is 15%) in the resin thrust washer 20B having the oil grooves 25 connected so as to draw a substantially V shape, Comparative Example 61 When the groove angle is 60 degrees, it interferes with other oil grooves 25, so that it cannot be manufactured. However, when the groove angle of the oil groove 25 is in the range of 30 degrees to 55 degrees, the average torque is as small as 0.2 Nm or less and the wear amount is as small as 30 μm or less, which is preferable.

(9) Regarding the experimental results regarding the groove angle when the sliding area ratio is 70% (oil groove area ratio is 30%) in the resin thrust washer 20B according to the fourth configuration example, FIG. 17 and FIG. 18 show. An experiment was conducted by attaching a resin thrust washer 20B having a sliding area ratio of 70% (oil groove area ratio of 30%) to the above-mentioned load measuring device 300 as shown in the fourth configuration example. The experimental results are shown in Table 8. Table 8 shows the torque (sliding load), the amount of wear, and the determination results (torque determination and wear amount determination) when the groove angle is changed. In Table 8, the case where the groove angle of the oil groove 25 is 30 degrees corresponds to the embodiment 71, the case where the groove angle of the oil groove 25 is 40 degrees corresponds to the embodiment 72, and the groove angle of the oil groove 25 corresponds to the embodiment 72. 45 degrees corresponds to Example 73, the groove angle of the oil groove 25 corresponds to Example 74, and the groove angle of the oil groove 25 corresponds to Example 75. The case where the groove angle of the oil groove 25 is 60 degrees corresponds to Comparative Example 71.

The judgment criteria for torque judgment in Table 8 are "A" when the torque is 0.2 Nm or less, "B" when the torque is larger than 0.2 Nm, and "C" when the resin thrust washer 20B cannot be manufactured. The criteria for determining the amount of wear are "A" when the amount of wear is 30 μm or less, "B" when the amount is larger than 30 μm, and "C" when the resin thrust washer 20B cannot be manufactured. It is the same as the case of. In the torque determination and the wear amount determination in Table 8, there is no determination "B", and the determination "A" and the determination "C" exist.

In such an experimental result, when the sliding area ratio is 70% (that is, the oil groove area ratio is 30%) in the resin thrust washer 20B having the oil grooves 25 connected so as to draw a substantially V shape, Comparative Example 71. When the groove angle is 60 degrees, it interferes with other oil grooves 25, so that it cannot be manufactured. However, when the groove angle of the oil groove 25 is in the range of 30 degrees to 55 degrees, the average torque is as small as 0.2 Nm or less and the wear amount is as small as 30 μm or less, which is preferable.

(10) Regarding the experimental results regarding the groove angle when the sliding area ratio is 60% (oil groove area ratio is 40%) in the resin thrust washer 20B according to the fourth configuration example, FIG. 17 and FIG. 18 show. An experiment was conducted by attaching a resin thrust washer 20B having a sliding area ratio of 60% (oil groove area ratio of 40%) to the above-mentioned load measuring device 300 as shown in the fourth configuration example. The experimental results are shown in Table 9. Table 9 shows the torque (sliding load), the amount of wear, and the determination results (torque determination and wear amount determination) when the groove angle is changed. In Table 9, the case where the groove angle of the oil groove 25 is 30 degrees corresponds to the embodiment 81, the case where the groove angle of the oil groove 25 is 40 degrees corresponds to the embodiment 82, and the groove angle of the oil groove 25 corresponds to the embodiment 82. 45 degrees corresponds to Example 83, the groove angle of the oil groove 25 corresponds to Example 84, and the groove angle of the oil groove 25 corresponds to Example 85. The case where the groove angle of the oil groove 25 is 60 degrees corresponds to Comparative Example 81.

The judgment criteria for torque judgment in Table 9 are "A" when the torque is 0.2 Nm or less, "B" when the torque is larger than 0.2 Nm, and "C" when the resin thrust washer 20B cannot be manufactured. The criteria for determining the amount of wear are "A" when the amount of wear is 30 μm or less, "B" when the amount is larger than 30 μm, and "C" when the resin thrust washer 20B cannot be manufactured. It is the same as the case of. In the torque determination and the wear amount determination in Table 9, there is no determination "B", and the determination "A" and the determination "C" exist.

In such an experimental result, when the sliding area ratio is 60% (that is, the oil groove area ratio is 40%) in the resin thrust washer 20B having the oil grooves 25 connected so as to draw a substantially V shape, Comparative Example 81 When the groove angle is 60 degrees, it interferes with other oil grooves 25, so that it cannot be manufactured. However, when the groove angle of the oil groove 25 is in the range of 30 degrees to 55 degrees, the average torque is as small as 0.2 Nm or less and the wear amount is as small as 30 μm or less, which is preferable.

(11) Experimental Results When Oil Grooves 25 Are Formed on Both Sides of Resin Thrust Washers 20A and 20B According to Third, Fifth to Eleventh Configuration Examples Next, Third, Fifth to Eleventh Configuration Examples An experiment was conducted by attaching the resin thrust washers 20A and 20B having oil grooves formed on both sides to the above-mentioned load measuring device 300. In this experiment, resin thrust washers 20A and 20B having a sliding area ratio of 70% (oil groove area ratio of 30%) and a groove angle of 45 degrees were used. The results of this experiment are shown in Table 10. In Table 10, the torque (sliding load), the amount of wear, and the judgment results (torque judgment and wear amount judgment) when the resin thrust washers 20A and 20B to be attached are changed. It is shown.

In Table 10, the case of the resin thrust washer 20A according to the third configuration example corresponds to the embodiment 91, the case of the resin thrust washer 20A according to the fifth configuration example corresponds to the embodiment 92, and the sixth configuration example. The case of the resin thrust washer 20A according to the configuration example corresponds to the embodiment 93, the case of the resin thrust washer 20A according to the seventh configuration example corresponds to the embodiment 94, and the case of the resin thrust washer 20A according to the eighth configuration example corresponds to the eighth configuration example. The case of 20A corresponds to Example 95, the case of the resin thrust washer 20A according to the ninth configuration example corresponds to Example 96, and the case of the resin thrust washer 20A according to the tenth configuration example corresponds to Example 97. Correspondingly, the case of the resin thrust washer 20A according to 11 configuration examples corresponds to Example 98.

In addition, the judgment standard for torque judgment in Table 10 is "A" when it is 0.6 Nm or less, and "B" when it is larger than 0.6 Nm, and the judgment standard for wear amount judgment is 30 μm or less. The case is "A", and the case larger than 30 μm is “B”.

According to the experimental results, the resin thrust washers 20A and 20B according to the third, fifth and eleventh configuration examples, and the average torque of any of the resin thrust washers 20A and 20B having oil grooves 25 on both sides. Is as small as 0.6 N · m or less, and the amount of wear is as small as 30 μm or less, which is preferable.

[6. Action effect]
The resin thrust washer 20 having the above configuration is provided with a sliding surface 26 that slides on the front surface and the back surface of the ring-shaped portion 21 with other members (counterparts C1, C2 and other thrust washers). Further, at least one of the front surface and the back surface is provided with an oil groove 25 that is recessed from the sliding surface 26 and allows lubricating oil to enter. The oil groove 25 has an opening 27 at the inner peripheral end of the ring-shaped portion 21, which is recessed from the sliding surface 26 and allows lubricating oil to enter from the insertion hole 22 side. At the outer peripheral end of the ring-shaped portion 21 of one oil groove 25, the lubricating oil that separates the oil groove 25 from the outside of the ring-shaped portion 21 and has entered the oil groove 25 flows out to the outer peripheral side of the ring-shaped portion 21. An oil stop wall 28 is provided to prevent the oil from rising. The position of the resin thrust washer 20 of the oil stop wall 28 in the thickness direction is provided at a position similar to that of the sliding surface 26, and the oil groove area ratio is provided within the range of 15% to 40%. There is.

Therefore, the lubricating oil that has entered the oil groove 25 is prevented from flowing out to the outer peripheral side of the resin thrust washer 20 by the oil stop wall 28. Therefore, on the surface side of the resin thrust washer 20 where the oil groove 25 exists, an oil film of lubricating oil can be easily formed between the resin thrust washer 20 and other members (counterparts C1 and C2 and other thrust washers). It will be possible. Further, the oil groove area ratio is provided in the range of 15% to 40%. Therefore, as is clear from the experimental results of Tables 32 to 34 and Tables 1 to 10, the surface side of the resin thrust washer 20 where the oil groove 25 exists and other members (counterparts C1, C2 and others). It is possible to reduce the sliding load with the thrust washer).

Further, in the present embodiment, at the intersection position where the center line L2 of the oil groove 25 and the center line L1 in the radial direction of the ring-shaped portion 21 intersect, the radial line L3 passes through the intersection position and along the radial direction. On the other hand, the inclination angle θ1 formed by the center line L2 of the oil groove 25 is preferably provided in the range of 30 degrees to 55 degrees.

With such a configuration, as is clear from the experimental results shown in Tables 1 to 10, it is possible to further reduce the wear amount and the average torque (sliding load) of the resin thrust washer 20A. ..

Further, in the present embodiment, the oil groove 25 guides the lubricating oil that has entered the oil groove 25 to the sliding surface 26, and the sliding surface 26 and other members (counterparts C1, C2 and other members). It is preferable that a dynamic pressure guide wall surface 254 for generating dynamic pressure is provided adjacent to the thrust washer).

As described above, when the dynamic pressure guide wall surface 254 as shown in FIGS. 15 and 16 is provided adjacent to the oil groove 25, the average torque (sliding load) of the resin thrust washer 20A can be further reduced. It will be possible.

Further, in the present embodiment, the oil groove 25 includes a first oil groove 25c that is inclined to one side with respect to the radial direction of the ring-shaped portion 21, and one side with respect to the radial direction of the ring-shaped portion 21. It is preferable that the second oil groove 25d is provided on the other side, which is different from the above, and the first oil groove 25c and the second oil groove 25d are connected by an opening 27.

In this configuration, the first oil groove 25c and the second oil groove 25d are inclined to one side and the other side with a radial direction in between. Therefore, on the surface side of the resin thrust washer 20B where the oil groove 25 exists, regardless of whether the resin thrust washer 20B rotates clockwise or counterclockwise, other members (counterpart materials C1, C2 and others) An oil film made of lubricating oil can be easily formed between the thrust washer and the thrust washer. Therefore, regardless of the rotation direction of the resin thrust washer 20B, between the surface side of the resin thrust washer 20B where the oil groove 25 exists and another member (the mating materials C1 and C2 and other thrust washers). It is possible to reduce the sliding load.

Further, in the present embodiment, the first oil groove 25c and the second oil groove 25d are provided with a bottom portion 251 most recessed from the sliding surface 26, respectively, and the first oil groove 25c and the second oil groove 25d are provided. Is provided with a tapered wall surface 252 that is linearly inclined toward the sliding surface 26 at a portion located outside not surrounded by the first oil groove 25c and the second oil groove 25d. , It is preferable that the bottom portion 251 is provided wider than the bottom portion 251.

In this configuration, the wide tapered wall surface 252 guides the lubricating oil that has entered the oil groove 25 to the sliding surface 26, so that the resin thrust washer 20 and other members (counterparts C1 and C2) And other thrust washers) can further reduce the sliding load.

Further, in the present embodiment, the first oil groove 25c and the second oil groove 25d are provided with a curved wall surface 255 that is curved so as to have an inflection point from the bottom portion 251 toward the sliding surface 26. Is preferable.

In this configuration, the curved wall surface 255 guides the lubricating oil that has entered the oil groove 25 to the sliding surface 26, so that the resin thrust washer 20 and other members (counterparts C1, C2, etc.) It is possible to further reduce the sliding load between the thrust washer and the thrust washer.

[6. Modification example]
Although each embodiment of the present invention has been described above, the present invention can be variously modified in addition to the above. This will be described below.

In the above-described embodiment, oil grooves 25 having the same shape are provided on the front surface and the back surface of one resin thrust washer 20. However, the oil grooves 25 formed on the front surface and the back surface of one resin thrust washer 20 may have different shapes. Further, at least one of the oil grooves 25 formed in the resin thrust washer 20 constituting the combination thrust washer 10 may have a shape different from the others. For example, an appropriate amount of lubricating oil is supplied according to the surface roughness of the surface facing the sliding surface 26 where the oil groove 25 exists, such as the resin thrust washer 20, the metal thrust washer, and the mating materials C1 and C2. The shape of the oil groove 25 may be changed so as to be performed.

In addition, specific values of the dimensions of the oil groove 25 of each configuration example of the above-described embodiment are shown as an example. However, the oil groove 25 may adopt other dimensional values.

Further, in the oil groove 25 in each of the above-described embodiments, the oil groove 25 along the radial direction and the oil groove 25 inclined at a predetermined inclination angle with respect to the radial direction may coexist. Examples of such configurations are shown in FIGS. 36 and 37. The resin thrust washer 20B (12th configuration example) shown in FIG. 36 has a convex curved surface portion 256, a wide groove portion 257, and a convex curved surface portion 256, similarly to the resin thrust washer 20B according to the eighth configuration example as shown in FIGS. 25 and 26. It has a narrow groove portion 258. Further, a communication oil groove 25b is provided at a portion between the first oil groove 25c and the second oil groove 25d of one set. So to speak, in the portion between the first oil groove 25c and the second oil groove 25d which are separated from each other (not connected by the opening 27), the communication oil groove 25b (intermediate communication oil groove) as shown in FIG. 36 Corresponding to) is provided.

In such a configuration, in addition to the non-communication oil groove 25a, a communication oil groove 25b that communicates with the outside of the ring-shaped portion 21 without the presence of the oil stop wall 28 is provided. Lubricating oil flows from the inner diameter side to the outer diameter side through the communication oil groove 25b. Therefore, the heat generated by the sliding of the resin thrust washer 20 can be released to the outside through the lubricating oil. Therefore, it is possible to improve the heat dissipation of the resin thrust washer 20, and it is possible to prevent the resin thrust washer 20 from being melted due to heat accumulation in the resin thrust washer 20.

Further, the communicating oil groove 25b is arranged between the openings 27 adjacent to each other in the circumferential direction of the ring-shaped portion 21 so as not to interfere with the first oil groove 25c and the second oil groove 25d. Therefore, the non-communication oil groove 25a (first oil groove 25c and second oil groove 25d) for reducing the sliding load and the communicating oil groove 25b for releasing heat to the outside are arranged on the sliding surface 26 in a well-balanced manner. Can be realized.

Further, the non-communication oil groove 25a is provided with a wide groove portion 257 and a narrow groove portion 258 having a groove width narrower than that of the wide groove portion 257, and the narrow groove portion 258 is connected to the opening 27. Further, the wide groove portion 257 is continuous with the wide groove portion 257 and is provided on the oil stop wall 28 side. Therefore, the sliding load can be satisfactorily reduced.

Further, between the non-communication oil grooves 25a (the first oil groove 25c and the second oil groove 25d) that are separated from each other, the oil stop wall 28 does not exist and communicates with the outside of the ring-shaped portion 21. A communication oil groove 25b (intermediate communication oil groove) is provided. Therefore, the non-communication oil groove 25a (first oil groove 25c and second oil groove 25d) for reducing the sliding load and the communicating oil groove 25b for releasing heat to the outside are provided on the sliding surface 26 in a well-balanced manner. The configuration to be arranged can be realized.

Further, the resin thrust washer 20A (13th configuration example) shown in FIG. 37 has a sliding protrusion 112 and continuous oil, similarly to the resin thrust washer 20A according to the 9th configuration example as shown in FIGS. 27 and 28. It has a groove 113 and a dynamic pressure guide wall surface 254. Further, a communicating oil groove 25b is provided between the non-communication oil grooves 25a adjacent to each other in the circumferential direction.

In such a configuration, the non-communication oil groove 25a and the communication oil groove 25b are alternately provided in the circumferential direction of the ring-shaped portion 21. Therefore, both reduction of sliding load and good heat dissipation can be realized.

Further, the communication oil groove 25b has a communication existing between a communication oil groove 113 (adjacent communication oil groove) provided adjacent to the non-communication oil groove 25a and a non-communication oil groove 25a separated from each other. An oil groove 25b (intermediate communication oil groove) is provided. Therefore, the heat dissipation of the resin thrust washer 20A can be further improved.

In FIG. 36, one communicating oil groove 25b is arranged between the openings 27 adjacent to each other in the circumferential direction of the ring-shaped portion 21 without interfering with the first oil groove 25c and the second oil groove 25d. ing. However, two or more communicating oil grooves 25b may be arranged between the openings 27 adjacent to each other in the circumferential direction. Further, the communication oil groove 25b may not exist at one or more of the openings 27 adjacent to each other in the circumferential direction. Further, the arrangement of the communication oil grooves 25b may be a regular arrangement in the circumferential direction, or may be an irregular arrangement. Further, in at least one of the configurations shown in FIGS. 36 and 37, the dynamic pressure guide wall surface 254 may not be provided.

In the present invention, the above-mentioned examples and dimensional examples are merely examples, and as long as it is within the above-mentioned sliding area ratio (oil groove area ratio), the above-mentioned examples and dimensional examples may be applied. Of course, it can be included in the present invention.

10 ... Combination thrust washer, 20, 20A, 20B ... Resin thrust washer, 21 ... Ring-shaped part, 22 ... Insertion hole, 23 ... Oil introduction groove, 24 ... Oil scooping surface, 25 ... Oil groove, 25a ... Non-continuous oil Groove, 25b ... Communication oil groove, 25c ... First oil groove, 25d ... Second oil groove, 26 ... Sliding surface, 27 ... Opening, 28, 110a ... Oil stop wall, 109 ... Oil embankment, 110 ... Branch Oil groove, 111 ... Surrounding part, 112 ... Sliding protrusion, 113 ... Communication oil groove (corresponding to adjacent communication oil groove), 114 ... Oil reservoir groove, 114a ... First oil reservoir groove, 114b ... Second oil reservoir groove, 115 ... Bottom, 116 ... Tapered wall surface, 251 ... Bottom, 252 ... Tapered wall surface, 253 ... Convex curved surface, 254 ... Dynamic pressure guide wall surface, 255 ... Curved wall surface, 256 ... Convex curved surface, 257 ... Wide groove, 258 ... Width Narrow groove, 259 ... Concave curved surface, 260 ... Concave curved surface, 261 ... Inclined wall, 300 ... Load measuring device, 301 ... Oil pan, 301a ... Inner cylinder, 301b ... Oil outlet, 302 ... Fixed shaft, 303 ... rotating shaft, 304 ... oil supply path, 305 ... thermocouple, 306,307 ... oil seal, S1-S3 ... thrust washer

Claims (16)

A thrust washer made of a resin-containing material having a ring-shaped portion surrounding the insertion hole.
The thrust washer is provided with sliding surfaces that slide with other members on the front surface and the back surface of the ring-shaped portion, and further, at least one of the front surface and the back surface is recessed from the sliding surface and lubricating oil enters. There is an oil groove,
The ring-shaped portion is closed between the front surface and the back surface without forming a hole penetrating the ring-shaped portion.
The oil groove is recessed from the sliding surface and has an opening on the inner peripheral end side of the ring-shaped portion that allows the lubricating oil to enter from the insertion hole side.
At the outer peripheral end of the ring-shaped portion of at least one oil groove, the lubricating oil that separates the oil groove from the outside of the ring-shaped portion and has entered the oil groove is placed on the outer peripheral side of the ring-shaped portion. An oil stop wall for suppressing the outflow is provided, and the position of the oil stop wall in the thickness direction of the thrust washer is provided at a position similar to the sliding surface.
The sliding area ratio occupied by the sliding surface with respect to the projected surface in the plan view of the ring-shaped portion is provided in the range of 60 to 85%.
Thrust washer that is characterized by that. The thrust washer according to claim 1.
At the intersection position where the center line of the oil groove and the center line passing through the center between the inner peripheral end portion and the outer peripheral end portion of the ring-shaped portion intersect, the intersection position is passed and the ring-shaped portion passes in the radial direction. The inclination angle formed by the center line of the oil groove with respect to the radial line along the line is provided in the range of 30 degrees to 55 degrees.
Thrust washer that is characterized by that. The thrust washer according to claim 1 or 2.
The oil groove is adjacent to a dynamic pressure guide wall surface for guiding the lubricating oil that has entered the oil groove to the sliding surface to generate dynamic pressure between the sliding surface and another member. Provided,
Thrust washer that is characterized by that. The thrust washer according to any one of claims 1 to 3.
The oil groove has a first oil groove that is inclined to one side with respect to the radial direction of the ring-shaped portion and an oil groove that is inclined to the other side different from the one side with respect to the radial direction of the ring-shaped portion. There is a second oil groove that is
The first oil groove and the second oil groove are connected by the opening.
Thrust washer that is characterized by that. The thrust washer according to claim 4.
The first oil groove and the second oil groove are each provided with a bottom portion that is most recessed from the sliding surface.
Wherein the first oil groove and the second oil groove, the first oil groove and said first oil surrounded by sites with the second oil grooves being connected with said opening being connected with the opening When the inside of the groove in the width direction and the inside of the second oil groove in the width direction, the portion located inside the groove and the outside of the first oil groove on the opposite side in the width direction, and the inside and the first oil groove. 2 A tapered wall surface that is linearly inclined toward the sliding surface is provided at a portion of the oil groove located on the outer side on the opposite side in the width direction.
The tapered wall surface is provided wider than the bottom portion.
Thrust washer that is characterized by that. The thrust washer according to claim 5.
The first oil groove and the second oil groove are provided with a curved wall surface that is curved so as to have an inflection point from the bottom portion toward the sliding surface.
Thrust washer that is characterized by that. The thrust washer according to any one of claims 1 to 6.
The oil groove includes a non-communication oil groove separated from the outside of the ring-shaped portion by the oil stop wall and a communication oil groove that communicates with the outside of the ring-shaped portion without the oil stop wall. Is provided,
Thrust washer that is characterized by that. The thrust washer according to claim 7.
The non-communication oil groove and the communication oil groove are alternately provided in the circumferential direction of the ring-shaped portion.
Thrust washer that is characterized by that. The thrust washer according to claim 7.
The communicating oil groove is provided with an adjacent communication oil groove provided adjacent to the non-communication oil groove and an intermediate communication oil groove existing between the non-communication oil grooves separated from each other. Yes,
Thrust washer that is characterized by that. The thrust washer according to claim 4.
The oil groove includes a non-communication oil groove separated from the outside of the ring-shaped portion by the oil stop wall and a communication oil groove that communicates with the outside of the ring-shaped portion without the oil stop wall. And are provided,
The communicating oil groove is arranged at a portion between the openings adjacent to each other in the circumferential direction of the ring-shaped portion without interfering with the first oil groove and the second oil groove.
Thrust washer that is characterized by that. The thrust washer according to claim 10.
The non-communication oil groove is provided with a wide groove portion and a narrow groove portion having a groove width narrower than that of the wide groove portion.
The narrow groove portion is connected to the opening and is connected to the opening.
The wide groove portion is continuous with the narrow groove portion and is provided on the oil stop wall side.
Thrust washer that is characterized by that. The thrust washer according to claim 11.
Between the non-communication oil grooves that are separated from each other, an intermediate communication oil groove that does not exist and communicates with the outside of the ring-shaped portion is provided.
Thrust washer that is characterized by that. The thrust washer according to any one of claims 1 to 12.
An oil scooping surface for guiding the lubricating oil to the opening is provided on the inner peripheral side of the ring-shaped portion.
The oil scooping surface is provided so as to be inclined with respect to the axial direction of the ring-shaped portion.
The opening is formed by recessing the oil scooping surface.
Thrust washer that is characterized by that. The thrust washer according to claim 13.
The height from the inner peripheral end of the oil scooping surface to the sliding surface is at least twice the height from the bottom of the oil groove, which is the most recessed from the sliding surface, to the sliding surface. Provided in the dimensions of
Thrust washer that is characterized by that. The thrust washer according to claim 13 or 14.
The ring-shaped portion is provided with an oil introduction groove recessed from the inner diameter side to the outer diameter side of the ring-shaped portion.
The inclination angle formed by the bottom of the oil introduction groove with respect to the axial direction of the ring-shaped portion is smaller than the inclination angle formed by the oil scooping surface with respect to the axial direction.
A step is provided between the oil introduction groove and the oil scooping surface.
Thrust washer that is characterized by that. The thrust washer according to claim 15.
Of the oil introduction grooves, at least a part of the boundary wall with the oil scooping surface is provided so as to be inclined with respect to the radial direction of the ring-shaped portion.
Thrust washer that is characterized by that.

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