JP2012180884A - Rotation supporting device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve a structure which effectively prevents a bearing ring of a thrust race 4 or the like from creeping with respect to a mating member such as a shaft member while curbing the cost thereof and making up a compact and light-weight constitution.SOLUTION: A wet type paper friction material 27 is stuck to a counter-raceway surface 26 of a race section 24 of the thrust race 4. The wet type paper friction material 27 is sandwiched and retained between the counter-raceway surface 26 and the axial end surface of the mating member.

Description

  The present invention relates to an improvement of a rotation support device that constitutes a rotation support portion of various mechanical devices. The bearing ring of a rolling bearing is a member to be rotated together with the race ring, or a member that should remain stationary with the race ring. A structure capable of effectively preventing creep, which is a phenomenon of relative rotation, is realized at low cost. For example, in order to support the thrust load applied to the rotating part of the transmission of an automobile, the thrust bearing ring constituting the thrust roller bearing (including the thrust needle bearing) used in the state assembled to the rotating part is This is a preferred invention for preventing relative rotation.

  For example, a thrust roller bearing as described in Patent Documents 1 to 3 is mounted on a rotating portion of a transmission or the like so as to support a thrust load applied to a rotating shaft or the like. 6 to 7 show an example of a thrust roller bearing 1 that has been widely known. The thrust roller bearing 1 includes a plurality of rollers 2 arranged in a radial direction, a cage 3 that holds the rollers 2, and a pair of thrust traces 4 and 5 that clamp the rollers 2 from both sides. Become. The cage 3 is formed by radially arranging the same number of pockets 6 as the rollers 2. The rollers 2 are prevented from falling out of the pockets 6 based on the engagement between the respective rolling surfaces and the opening edges of the pockets 6 while being held in the pockets 6. ing.

  Each of the thrust traces 4 and 5 is made of a hard metal plate having sufficient hardness, such as bearing steel or case-hardened steel, and has a short cylindrical flange on the inner or outer periphery. 7 and 8 are formed. And, by bending the distal end portions of the flange 7 arranged radially inside among them radially outwardly and by bending the distal end portions of the flange 8 arranged radially outside radially inward, respectively. The locking projections 9 and 10 are used. The engaging protrusions 9 and 10 and the inner peripheral edge or the outer peripheral edge of the retainer 3 are engaged with each other, so that the components of the thrust roller bearing 1 are connected to each other without separation. Further, a plurality of tip end portions of the flange 8 arranged on the outer side in the radial direction are bent outward in the radial direction to form the reverse assembly preventing projections 11, 11.

  The thrust roller bearing 1 as described above is mounted, for example, on the rotating portion where the thrust load is generated in a state where the thrust trace 5 is fitted in a circular holding recess 13 formed in the casing 12. In this state, of the both side surfaces in the axial direction of the thrust trace 5, the side surface opposite to the thrust raceway surface with which the rolling surface of the roller 2 is in contact (the right side surface in FIG. 6) is the back of the holding recess 13. The side surface (the left side surface in FIG. 6) opposite to the thrust raceway surface with which the rolling surface of the roller 2 is in contact, of the two axial side surfaces of the other thrust trace 4, is in contact with the surface 14. Abutting on the end face 16. As a result, the mating member 15 is rotatably supported with respect to the casing 12 and a thrust load acting between the members 12 and 15 is supported.

  Further, for example, a radial rolling bearing is widely used in order to rotatably support a rotating shaft inside a housing while supporting a radial applied to the rotating shaft. The radial rolling bearing is provided on an inner ring raceway 18 provided on the outer peripheral surface of the inner ring 17 and an inner peripheral surface of the outer ring 19 as shown in FIG. 5 showing a second example of an embodiment of the present invention described later. A plurality of rolling elements (balls) 21, 21 are provided between the outer ring raceway 20 and the outer ring raceway 20 so as to be freely rollable while being held by a cage 22. Such a radial rolling bearing 23 is configured such that, for example, the outer ring 19 is fitted and fixed to the housing, and the inner ring 17 is fitted and fixed to the rotating shaft, so that the rotating shaft is rotatably supported on the inner diameter side of the housing. .

  Even if it is a rotation support device incorporating the thrust roller bearing 1 as described above or a rotation support device incorporating the radial rolling bearing 23 as described above, in order to ensure durability, a rolling bearing (thrust roller) is required. The bearing rings (thrust traces 4, 5, inner ring 17, outer ring 19) constituting the bearing 1 and the radial rolling bearing 23) must be prevented from shifting (relatively rotating) with respect to the counterpart member supporting the bearing ring. There is. That is, during operation of the rotation support device, the force in the direction of rotating (creeping) the bearing ring relative to the counterpart member based on the rotational resistance (dynamic torque) of the rolling bearing and the elastic deformation of the bearing ring. Will be added. Of these, the force applied based on the dynamic torque is well known, and even the force applied based on the elastic deformation of the raceway is described in, for example, Patent Document 4 and has been conventionally known.

  In any case, when creep occurs as the bearing ring rotates relative to the mating member, the contact portion between the bearing ring and the mating member wears. Generally, this bearing ring is made of an iron-based hard metal such as high carbon chromium bearing steel, case-hardened steel, or high speed steel. On the other hand, the mating member may be a hard metal such as high-speed steel, but is generally softer than the metal material constituting the bearing ring, such as a light metal such as medium carbon steel or an aluminum alloy. Made of metal. For this reason, when the creep occurs, a portion of the mating member that is in contact with the race is worn. As a result, with use over a long period of time, the rotation support part incorporating the rolling bearing becomes rattled, or the generated wear powder promotes wear of other parts such as the inside of the rolling bearing. May cause problems.

  As a countermeasure for preventing the occurrence of creep that causes such a problem, Patent Document 4 describes that the thickness of the thrust trace constituting the thrust roller bearing is secured to a predetermined value or more. For example, in the case of a rotation support portion of a general compressor for a car air conditioner, it is possible to prevent the thrust trace from creeping against the mating member by ensuring the thickness of the thrust trace. However, due to the recent reduction in size and weight of various rotating machinery equipment such as compressors for car air conditioners, the installation space for thrust roller bearings has also decreased, and the sectional height (axial dimension) of this thrust roller bearing is also reduced. It is often required to make it smaller. In such a case, there is a possibility that a sufficient thickness of the thrust trace cannot be secured. By providing an uneven engagement portion between this thrust trace and the mating member, the occurrence of the creep can be prevented even if this thrust trace is thin, but not only is disadvantageous in terms of miniaturization and weight reduction, This will increase production costs.

  Patent Documents 5 to 12 describe various structures for preventing the race ring (particularly the outer ring) constituting the radial rolling bearing from creeping with respect to the mating member (housing). Of these, Patent Document 5 describes a structure in which a rough surface provided on an annular creep prevention member engaged with an outer ring is pressed against a housing. Patent Document 6 describes a structure in which a ring-shaped eccentric ring attached to an eccentric groove formed on the outer peripheral surface of the outer ring is wedged between the bottom surface of the eccentric groove and the inner peripheral surface of the housing. Has been. Patent Document 7 describes a structure in which an O-ring attached to a locking groove formed on the outer peripheral surface of the outer ring is elastically sandwiched between the bottom surface of the locking groove and the inner peripheral surface of the housing. ing. In Patent Documents 8, 9, and 11, a synthetic resin ring attached to a locking groove formed on the outer peripheral surface of the outer ring is attached to the bottom surface of the locking groove and the inner peripheral surface of the housing as the temperature rises. The structure which makes it stretch between is described. Patent Document 10 describes a structure in which the outer peripheral surface of the outer ring and the inner peripheral surface of the housing are bonded. Furthermore, Patent Document 12 describes a structure in which an annular member having a special composition is sandwiched between the outer peripheral surface of the outer ring and the inner peripheral surface of the housing.

  In the case of the conventional structures described in Patent Documents 5 to 12 as described above, it is possible to prevent creeping of the bearing ring constituting the radial rolling bearing, but it is possible to prevent creeping of the thrust trace by applying to the thrust rolling bearing. difficult. In addition to the structure described in Patent Documents 5 and 12, even when applied to a radial rolling bearing, the outer ring is formed with a concave groove such as an eccentric groove or a locking groove on the outer peripheral surface of the outer ring. In addition to increasing the processing cost, it is disadvantageous in terms of securing the strength of the outer ring. Furthermore, the structures described in Patent Documents 5 and 12 are only disadvantageous from the viewpoint of miniaturization and weight reduction because of the use of a creep preventing member having a certain thickness in order to ensure the necessary rigidity. In addition, parts manufacturing, parts management, and assembly work are all complicated, and it is inevitable that costs increase.

  Conventionally, wet paper friction materials as described in Patent Documents 13 to 16 are known as materials for increasing the frictional force between the mating surfaces. The wet paper friction material is made by, for example, impregnating a papermaking body with a thermosetting synthetic resin, heat-curing, and further press-molding, and is thin and has a certain friction coefficient. However, conventionally, as a use of such a wet paper friction material, only a clutch plate of a wet multi-plate clutch incorporated in an automatic transmission for automobiles has been proposed.

JP 50-119145 A JP 2004-28342 A No. 7-16101 JP 2007-16965 A JP-A-8-326754 JP-A-10-82428 JP 2001-27255 A JP 2003-287043 A JP 2007-315585 A JP 2010-216580 A JP 2010-249194 A JP 2011-21676 A Japanese Patent Application Laid-Open No. 2004-346988 JP 2008-189749 A JP 2010-116440 A JP 2010-209216 A

  In view of the circumstances as described above, the present invention suppresses costs by proposing a completely new application as a paper friction material such as a wet paper friction material, such as creep prevention of a bearing ring constituting a rolling bearing. However, the invention has been invented to realize a structure that can be made small and light and can effectively prevent the race from creeping with respect to the mating member.

The rotation support device of the present invention includes first and second members that are arranged so as to be capable of relative rotation with each other, and a rolling bearing that is installed between the surfaces of these members facing each other.
The rolling bearing includes at least one raceway ring provided independently of the first and second members, and a plurality of rolling elements.
Further, the raceway ring is provided with a raceway surface for rolling contact with each of the rolling elements, and a surface other than the raceway surface is made of any one of the first and second members. It is assembled to this one member in a state of being engaged with a part of the surface (directly or through a paper friction material such as a wet paper friction material described below).
In particular, in the rotation support device of the present invention, a paper friction such as a wet paper friction material is provided between a partial surface of one of the members and a surface other than the raceway surface of the raceway. The material is pinched.

According to the rotary support device of the present invention configured as described above, it can be configured to be small and lightweight while suppressing cost, and the race can be effectively prevented from creeping with respect to the counterpart member.
First, the prevention of creep can be achieved by sandwiching a paper friction material such as a wet paper friction material having a large friction coefficient between the bearing ring and the mating member.
Next, the cost can be reduced by preventing a creep by holding a paper friction material, which is inexpensive per se, between the raceway and a member for engaging the raceway. In other words, it is not necessary to form grooves, locking projections, etc. on the raceway ring made of hard metal, or to form a structure part engaging with these on the counterpart member. It can be suppressed.
Further, downsizing and weight reduction can be achieved by not requiring the thickness of the raceway to be larger than that originally required for the raceway to prevent creep. Also, the paper friction material used for preventing creep is sufficient to be thin, so that the entire rotation support device is hardly increased by providing this paper friction material.

Sectional drawing which shows the 1st example of embodiment of this invention. The perspective view which shows three examples of the shape of a thrust trace. The schematic diagram which shows two examples of the relationship between the direction of the fiber of a wet paper friction material, and the direction in which a press-fit direction and a creep force are added. Sectional drawing which shows another four examples of the shape of a thrust trace. Sectional drawing which shows the 2nd example of embodiment of this invention. The principal part sectional drawing which shows one example of the rotation support apparatus used as the object of this invention. The figure which took out the right side thrust trace of FIG. 6, and was seen from the left side of the same figure.

[First example of embodiment]
An embodiment in which the present invention is applied to a thrust roller bearing will be described with reference to FIGS. It should be noted that the feature of the present invention is that the bearing ring constituting the rolling bearing should not rotate relative to the bearing ring in a state where the bearing ring is mounted. It has a structure for preventing relative rotation (creep) with a member that does not rotate with the wheel. The structure and operation of the other parts are the same as those of the rotation support device incorporating the conventionally known various types of rolling bearings, including the structure shown in FIGS. Therefore, illustrations and descriptions of conventionally known structural parts are omitted or simplified, and the characteristic parts of the present invention will be mainly described below.

  The thrust race 4 constituting the thrust roller bearing 1 as shown in FIG. 6 is formed on the inner peripheral edge of the annular race portion 24 with the flange 7 bent at right angles to the race portion 24 over the entire circumference. It consists of The one surface (the right surface in FIG. 1) of the race portion 24 existing in the bending direction of the flange 7 is a raceway surface 25, and the other surface (the left surface in FIG. 1) is an anti-orbit surface 26. For example, as shown in FIG. 6 described above, such a thrust trace 4 abuts (contacts) the anti-orbital surface 26 against the axial end surface of the mating member via a wet paper friction material 27 described below. ing. Depending on the structure of the rotation support portion, the flange 7 may be externally fitted with an interference fit to a shaft portion provided in a part of the counterpart member.

  A wet paper friction material 27 formed by cutting a sheet-like material into a ring shape is attached to the anti-orbital surface 26 of the thrust trace 4 as described above with an adhesive as shown by a broken line in FIG. As this wet paper friction material 27, what was described in the above-mentioned patent documents 13-16 can be used, for example. Specifically, the wet paper friction material 27 includes a paper sheet (paper) as a core material and a synthetic resin impregnated in the paper sheet. Of these, the paper-like sheet is composed of fibers, a filler, and a friction modifier. Among these fibers, one or more selected from natural fibers such as cellulose, hemp, and wood pulp, organic synthetic fibers such as aromatic polyamide and polyphenol, and inorganic fibers such as carbon fibers, glass fibers, and ceramic fibers. Various types can be adopted. Further, as the filler, one to a plurality of types selected from diatomaceous earth, clay, wollastonite, silica, carbonate and the like can be adopted. Further, as the friction modifier, one or more types selected from synthetic resin particles, rubber particles, graphite, coke powder, and the like can be adopted. Furthermore, as the synthetic resin, one to a plurality of types selected from phenol resin, imide-modified resin, melamine-modified resin, oil-modified resin, and the like can be adopted. The wet paper friction material 27 is a sheet-like material obtained by kneading the above-mentioned fiber, the filler and the friction modifier into a sheet, heat-curing, and press-molding. Is obtained by cutting into an annular shape in accordance with the shape of the anti-orbital surface 26.

  Inside the wet paper friction material 27 as described above, innumerable (many) minute spaces (continuous pores) each having a pore diameter of several μm to several tens of μm exist in a dispersed state. The porosity of each of these micro spaces (the total volume of the micro spaces / apparent volume of the wet paper friction material 27) is about 30 to 70%. In the state where the thrust roller bearing 1 constituted by the thrust trace 4 to which such a wet paper friction material 27 is attached is incorporated in a rotation support portion of an automobile transmission (manual transmission or automatic transmission), for example. When this automobile transmission is operated, the lubricating oil {mission oil or automatic fluid (ATF)} enters the innumerable minute spaces. The shearing resistance applied to the lubricating oil that has entered the countless minute spaces in the state of adhering to the axial end surface of the mating member is the resistance against the movement of the axial end surface and the wet paper friction material 27. Become. Based on this resistance, the mating member and the thrust race 4 are prevented from rotating relative to each other (creep), and the axial end surfaces of the mating member and the anti-orbital surface 26 of the thrust trace 4 are worn. Can be prevented.

  In order to prevent the counterpart member and the thrust trace 4 from creeping by such a mechanism, the thickness of the wet paper friction material 27 is sufficiently set to the pore diameter of each minute space. It is necessary to make it thicker. When the thickness of the wet paper friction material 27 is less than 10 μm, each minute space opens on both sides of the wet paper friction material 27, and the entire wet paper friction material 27 is the anti-orbital surface. 26 easily peels off. Therefore, the thickness of the wet paper friction material 27 is preferably 10 μm or more, more preferably 20 μm or more. On the other hand, when the thickness of the wet paper friction material 27 exceeds 1000 μm (1 mm), the wet paper friction material 27 itself has a tendency to creep between the counterpart member and the thrust trace 4. Due to the applied shear force, delamination is likely to occur in the wet paper friction material 27. Therefore, the thickness of the wet paper friction material 27 is set to 1000 μm or less, preferably 500 μm or less. In addition, although the ratio of the part covered with the wet paper friction material 27 in the anti-orbital surface 26 is larger, the effect of preventing creep can be increased, but at least 10% or more, preferably 50% or more. However, even if it covers over 90%, the effect is saturated and the wet paper friction material 27 protruding from the anti-orbital surface 26 may easily fall off. Therefore, the ratio of the portion covered with the wet paper friction material 27 in the anti-orbital surface 26 is 10 to 90%, preferably 50 to 90%. However, the entire anti-orbit surface 26 may be covered with the wet paper friction material 27 as long as no major problem occurs even if the anti-orbit surface 26 is covered 100%.

  The type of adhesive used for attaching the wet paper friction material 27 to the anti-orbital surface 26 is not particularly limited. However, in consideration of the environment during use, an adhesive having oil resistance and heat resistance is used. use. For example, a thermosetting adhesive having oil resistance is kept at this temperature for an appropriate time and cured while the surfaces to be bonded are pressed against each other while being heated to 170 to 350 ° C. Regardless of the heating at the time of bonding, the material of the thrust trace 4, the type of adhesive, the heating temperature, the heating duration time, etc. are regulated so that the required hardness (for example, Hv 650 or more) can be secured. .

  Further, the direction in which the wet paper friction material 27 is attached to the anti-orbital surface 26 is not particularly limited. When sticking to this anti-orbital surface 26 which is a thrust plane, it is not particularly meaningful to regulate the sticking direction of the wet paper friction material 27. Regardless of which direction is applied, the average friction coefficient is obtained when it is applied to the entire circumference, and specifically, the friction coefficient μ is about 0.15 when used under lubrication by automatic fluid. On the other hand, it is affixed only to a part in the circumferential direction, or as shown by a chain line in FIG. 1, a wet paper friction material 27a is affixed to the inner peripheral surface of the flange 7, and this flange 7 is used as a shaft member. In the case of external fitting by interference fitting, it is preferable to regulate the arrangement direction of the fibers constituting the wet paper friction material 27a. That is, when the fibers constituting the paper-like sheet constituting the wet paper friction material 27a have different thicknesses and the respective arrangement directions are restricted, the resulting wet paper friction material 27a and the mating surface (shaft member) The direction of the friction coefficient with the outer peripheral surface of the substrate is caused.

  For example, in FIG. 3A, when the vertical fibers are thicker than the horizontal fibers, the horizontal friction coefficient (eg, 0.2) is greater than the vertical friction coefficient (eg, 0.1). growing. Therefore, when the wet paper friction material 27a cut into a strip is pasted on the inner peripheral surface of the flange 7, the horizontal direction in FIG. Axial direction. By restricting in this way, the resistance when the flange 7 with the wet paper friction material 27a attached to the inner peripheral surface is externally fitted to the shaft member is suppressed to a low level. The circumferential frictional force acting between the inner peripheral surface of 7 and the outer peripheral surface of the shaft member can be increased. As a result, both the ease of assembling the thrust trace 4 to the shaft member and the excellent anti-creep effect after assembly can be achieved. However, the thickness of the fibers can be made uniform, and the direction of the fibers relative to the circumferential direction and the axial direction of the flange 7 can be about 45 degrees as shown in FIG. In this case, the coefficient of friction related to the press-fitting direction of the flange 7 with respect to the shaft member and the coefficient of friction in the circumferential direction contributing to creep prevention are substantially the same (for example, about 0.15).

  Moreover, the thickness of the wet paper friction materials 27 and 27a is uniform, and the wet paper friction materials 27 and 27a are affixed to reduce the manufacturing cost of the wet paper friction materials 27 and 27a themselves. This is also preferable from the viewpoint of facilitating the work of assembling the thrust trace 4 to the mating member. However, there is a possibility that a gap based on an inevitable manufacturing error may exist in the combination part of the thrust trace 4 and the mating member, and therefore it is not always necessary to make the thickness uniform. Further, in relation to the thickness of the thrust trace 4, the thickness of the wet paper friction material 27, 27a is sufficiently larger than the thickness of the race portion 24 of the thrust trace 4 when arranged in the radial direction (radial direction). Make it smaller. The reason for this is to prevent delamination of the wet paper friction material 27a when the race is fitted to the mating member with a tight margin. On the other hand, in the case of arranging in the axial direction (thrust direction), the wet paper friction material 27 is only pressed in the thickness direction when the track ring is assembled to the mating member, and delamination occurs. Since there is no fear, the thickness of the wet paper friction material 27 may be slightly larger than the thickness of the flange 7 of the thrust trace 4.

Furthermore, the shape of the thrust trace is not limited to that shown in FIGS. 1 and 2A, the shape shown in FIGS. 2B and 2C, and FIGS. The thing of the shape shown to D) can be used.
Of these, the thrust trace 5 shown in FIG. 2B corresponds to that described on the right side of FIG. The wet paper friction materials 27 and 27a (see FIG. 1) are attached to the anti-orbit surface portion of the race portion 24a or the outer peripheral surface of the flange 8.
Further, the thrust trace 28 shown in FIG. 2C is a simple flat plate, and a wet paper friction material 27 (see FIG. 1) is stuck on the anti-orbital surface portion.
Also with respect to the four types of thrust traces 28a to 28d described in FIGS. 4A to 4D, wet paper friction materials 27 and 27a are affixed to portions that abut (fit) the mating member.

[Second Example of Embodiment]
An embodiment in which the present invention is applied to a radial rolling bearing will be described with reference to FIG. Since the structure of the radial rolling bearing 23 shown in FIG. 5 is the same as described above, the redundant description will be omitted, and the following description will focus on the features related to the present invention. When the present invention is applied to the radial rolling bearing 23, it is between the inner ring 17 and a shaft member that externally fixes the inner ring 17, or between the outer ring 19 and a housing that internally fixes the outer ring 19. A wet paper friction material is provided. For this purpose, for example, as shown in FIG. 5, wet paper friction materials 27 b and 27 b are attached to the inner peripheral surface of the inner ring 17 and the outer peripheral surface of the outer ring 19. For both wet paper friction materials 27b and 27b, a sheet-like material made as described above is cut into a strip shape and attached to the inner peripheral surface of the inner ring 17 and the outer peripheral surface of the outer ring 19. In this case, for example, as shown in FIG. 3A described above, the fiber arrangement direction is appropriately regulated to achieve both the easy fitting operation and the securing of the creep preventing effect. If the condition such that the axial end surface of the inner ring 17 or the outer ring 19 is strongly pressed against a part of the mating member is satisfied, the axial end surface of the inner ring 17 or the outer ring 19 and the mating member are Wet paper friction material can also be sandwiched.

The results of experiments conducted to confirm the effects of the present invention will be described. The conditions of this experiment are as follows.
Types of rolling bearings used: Thrust roller bearings Thrust roller bearing inner diameter: 50 mm
Also outer diameter: 80mm
Similarly, the pitch circle diameter of each roller: 65mm
Similarly, the outer diameter of each roller: 2.5mm
Same length: 8mm
Basic dynamic load rating of thrust roller bearing Ca: 31500N
Similarly, basic static load rating Coa: 183000N
Thrust lace thickness: 0.8mm
The material of the housing which is the mating member of the thrust trace: ADC52 (aluminum alloy, hardness = Hv150)
Difference between the outer diameter of the flange formed on the outer periphery of the thrust trace and the inner diameter of the housing (twice the radial thickness of the gap between the peripheral surfaces of both members): 100 μm
Test load Fa: 15750N (P / C = 0.5)
Rotational speed: 3000min ^-1
Lubricant used: ATF (viscosity at 100 ° C. is 10 cSt or less)
Test temperature: 120 ° C
Calculation life: 56 hours Specification of wet paper friction material: With the structure of FIG. 3 (B), the friction coefficient is 0.15
The test was conducted under the above-mentioned conditions, and the test was interrupted when 60 hours passed after the start of the test, and the presence or absence of creep and wear was visually confirmed. The results are shown in Table 1 below.

Consider the results of the experiment shown in Table 1.
First, in Example 1, a wet paper friction material having a thickness of 10 μm {plate thickness ratio (thrust trace thickness / wet paper friction material thickness) = 80} is provided on the anti-orbital surface (back surface) of the thrust trace. Affixed over the entire surface. In the case of Example 1 as described above, since the thickness of the wet paper friction material was the minimum necessary, the occurrence of a thrust trace creep was observed after 60 hours. However, the wear produced on the mating member, the housing, was as small as 0.01 mm. This level of wear has little effect on the function of the rotary machine incorporating the thrust rolling bearing. In addition, the cause which the said abrasion generate | occur | produced is because a part of said wet paper friction material was not peeled from the said back surface with progress of a test.

  Next, in Example 2, the area ratio of the wet paper friction material occupying the entire back surface was 10% (0.1) instead of the thickness of the wet paper friction material affixed to the back surface of the thrust trace being as slightly as 30 μm. And few. In the case of Example 2 as described above, the occurrence of creep of the thrust trace was recognized, but only the sliding trace was recognized on the back surface of this thrust trace, and the occurrence of wear on the mating member was not recognized.

  Next, in Example 3, the wet paper friction material has a thickness as thick as 30 μm, and the area ratio of the wet paper friction material to the entire back surface of the thrust trace is sufficient as 60%. For this reason, even after 60 hours, the thrust trace did not creep, and therefore the wear of the housing as the counterpart member did not occur.

  Next, in Example 4, a wet paper friction material having a thickness of 30 μm on the back surface of the thrust trace, and a wet paper friction material having a thickness of 50 μm between the outer peripheral surface of the flange and the inner peripheral surface of the housing, Each is attached to 20% of the entire circumference. In this case, no thrust trace creep occurred, and therefore no wear of the housing occurred.

  Next, for Examples 5, 6, 7, and 8, the thickness of the wet paper friction material affixed to the back surface of the thrust trace was 50 μm or 200 μm, and the area ratio was 30% to 80%. Further, in Examples 6 and 8, a wet paper friction material having a thickness of 100 μm was stuck on the outer peripheral surface of the flange, and this flange was pushed into the housing by an interference fit. In each of Examples 5 to 8, no thrust trace creep occurred, and therefore no wear of the housing occurred.

  In Example 9, the wet paper friction material affixed to the back surface of the thrust trace is sufficiently thick with a thickness of 500 μm, but the area ratio of the wet paper friction material in the entire back surface is as small as 10% (0.1). In the case of Example 9 as described above, the occurrence of thrust trace creep was observed after 60 hours, but the housing was not worn.

In Example 10, the thickness of the wet paper friction material affixed to the back surface of the thrust trace is sufficiently thick as 1000 μm, and the area ratio of the wet paper friction material occupying the entire back surface is sufficient as 50%, As the test progressed, a part of the wet paper friction material was not peeled off from the back surface, so that a thrust trace creep occurred. As a result, the housing slightly worn down to 0.01 mm. However, this level of wear has little effect on the function of the rotating machine device incorporating the thrust rolling bearing.
From the above results, it is preferable to regulate the thickness of the wet paper friction material adhered to the back surface of the thrust trace within a range of 30 μm to 500 μm. The area ratio is preferably 20% or more.

  When a thrust trace having a cylindrical flange at the outer peripheral edge is assembled to the holding recess of the housing, the radial thickness between the outer peripheral surface of these flanges and the inner peripheral surface of the holding recess is 0. A gap of about 01 to 0.4 mm is interposed (a thrust trace is fitted into the holding recess). For this reason, in a state before the assembly of the rotation support device is completed, the thrust trace is easily dropped from the holding recess, and the assemblability is impaired. For this reason, in the past, gel adhesive substances such as petroleum jelly and grease were applied to the back surface of the thrust trace and temporarily adhered, but the drop-off prevention effect is uncertain. . In order to ensure the drop-off preventing effect, a drop-preventing tab is provided at the front edge of the flange, and this tab is engaged with the locking groove on the housing side. However, in the case of such a structure, it is necessary to process these tabs and locking grooves, which increases the manufacturing cost of the rotation support device.

  On the other hand, as in the above-described Examples 4, 6, and 8, the outer peripheral surface of the flange (in the case of a structure in which the flange provided on the inner peripheral edge is externally fitted to the shaft member) is wet on the flange. If a wet paper friction material having a thickness of 10 to 1000 μm is affixed to two or more places on the entire circumference or intermittently in the circumferential direction, the wet paper friction material is assembled when the rotary support device is assembled. Due to the frictional force between the material and the peripheral surface of the mating member, the thrust trace can be prevented from being inadvertently prevented from falling off.

In contrast to Examples 1 to 10 as described above, Comparative Examples 1, 2, and 3 have wet paper friction materials that are too thin as 3, 5, and 7 μm, respectively. Peeling of the material was observed. The housings were relatively heavily worn at 0.7 mm, 0.5 mm, and 0.2 mm, respectively.
On the other hand, in Comparative Examples 4 and 5, since the thickness of the wet paper friction material was too thick, 1500 μm and 2000 μm, peeling of the wet paper friction material was observed after 60 hours. As for the housing, wear of 0.1 mm and 0.6 mm was recognized, respectively.

  The above description of the embodiment has been mainly focused on the case where the present invention is applied to a thrust roller bearing. In contrast, the present invention can be applied to thrust rolling bearings other than roller bearings and various radial rolling bearings. For example, a wet paper friction material is attached to the outer peripheral surface of the shell type outer ring constituting the shell type needle bearing, the outer peripheral surface of the shell type outer ring, and the inner peripheral surface of the housing in which the shell type outer ring is fitted. A wet paper friction material can be interposed between the two. Furthermore, although not within the technical scope of the present invention, a wet paper friction material as in the present invention is provided between the race of the sliding bearing and the mating member to prevent the race and the mating member from creeping. You can also do it.

DESCRIPTION OF SYMBOLS 1 Thrust roller bearing 2 Roller 3 Cage 4 Thrust trace 5 Thrust trace 6 Pocket 7 Flange 8 Flange 9 Locking protrusion 10 Locking protrusion 11 Protrusion for preventing reverse assembly 12 Casing 13 Holding recessed part 14 Back surface 15 Counterpart member 16 End surface 17 Inner ring 18 Inner ring raceway 19 Outer ring 20 Outer ring raceway 21 Rolling element 22 Cage 23 Radial rolling bearing 24, 24a Race part 25 Raceway surface 26 Anti-orbital surface 27, 27a, 27b Wet paper friction material 28, 28a, 28b, 28c, 28d Thrust trace

Claims (7)

The first and second members arranged so as to be capable of relative rotation with each other, and rolling bearings installed between the mutually facing surfaces of these members,
The rolling bearing includes at least one raceway ring provided independently of the first and second members, and a plurality of rolling elements,
The raceway is provided with a raceway surface for rolling contact with each of the rolling elements, and a surface other than the raceway surface is a part of either one of the first and second members. In the rotating support device assembled to this one member while being engaged with the surface,
A rotation support device, wherein a paper friction material is sandwiched between a partial surface of one of the members and a surface of the raceway other than the raceway surface.   The rotation support device according to claim 1, wherein the paper friction material is affixed to a surface other than the raceway surface of the raceway.   The raceway abuts a non-orbital surface, which is a surface opposite to the raceway surface, with a backup surface that is a partial surface of the first member, and between the anti-orbital surface and the backup surface. The rotation support device according to claim 1, wherein the paper friction material is sandwiched.   The rolling bearing is a thrust roller bearing, each rolling element is a roller, the race is a thrust trace, and the paper friction material is an axial one side of the thrust trace, and an axial direction of the first member. The rotation support device according to any one of claims 1 to 3, wherein the rotation support device is sandwiched between the end surface.   The rolling bearing is a thrust roller bearing, each of the rolling elements is a roller, the race is a thrust trace having a cylindrical flange at a peripheral portion, and the paper friction material is formed with a peripheral surface of the flange. The rotation support device according to any one of claims 1 to 3, wherein the rotation support device is sandwiched between the first member and the circumferential surface of the first member.   The rotation support device according to any one of claims 1 to 5, wherein the paper friction material has a thickness of 10 to 1000 µm.   7. The paper friction material according to claim 1, wherein the paper friction material is interposed in a portion of 10% or more of the mutually opposing surfaces of the partial surface of the member and the raceway. The rotation support apparatus described in the item.

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