JP2014181792A - Thrust roller bearing with races - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a thrust roller bearing with races, for increasing an eccentricity allowance for a pair of relatively rotating members while securing a separation preventing function between a cage 3 and each of first and second thrust races 4a, 5a, increasing the amount of lubricating oil to be distributed inside, and actualizing the construction to be good in handling and to secure a stable operating condition under severe service conditions.SOLUTION: The outer diameter of an outer diameter side flange 8a formed at the outer peripheral edge of a first thrust race 4a is set to be 40-120 mm and the inner diameter of an inner diameter side flange 11a formed at the inner peripheral edge of an inner diameter side flange 5a is set to be 30-80 mm so that an internal clearance is 1-2 mm. For this purpose, outer diameter side lock parts 9a are formed at the front edge of the outer diameter side flange 8a intermittently with respect to the circumferential direction.

Description

  This invention is an improvement of a thrust roller bearing with a race (including a thrust needle bearing) that is used in a state where it is assembled to a rotating support portion in order to support a thrust load applied to the rotating support portion of various rotating machines such as an automobile transmission. About. Specifically, while ensuring the function of preventing separation between the cage and the pair of thrust traces, the tolerance for the eccentricity of the pair of relatively rotating members is increased, and the amount of lubricating oil to be circulated inside is increased. By increasing the number, it is possible to realize a structure that is easy to handle and can secure a stable operation state even under severe use conditions.

  A thrust roller bearing as described in, for example, Patent Document 1 is attached to a rotation support portion of various rotating machines such as a transmission, and a thrust applied between a rotating member such as a rotating shaft and a stationary member such as a casing. The rotating member is allowed to rotate while supporting a load. In addition, when a pair of members that rotate relative to each other through such a thrust roller bearing is a material that is difficult to ensure the required hardness, it is difficult to process a required smooth surface. When it is troublesome, a thrust roller bearing with a race in which one cage and a plurality of rollers and two races are combined is used.

  FIG. 7 shows an example of a thrust roller bearing 1 with a race that has been widely known. As is well known, the thrust roller bearing with race 1 includes a plurality of rollers 2 arranged in a radial direction, a cage 3 for holding these rollers 2, and each of these rollers 2. The first and second thrust traces 4 and 5 are sandwiched from both sides with respect to the three axial directions. The cage 3 is formed in an annular shape as a whole, and is formed by arranging the same number of pockets 6 as the rollers 2 radially at equal intervals in the circumferential direction.

  The first and second thrust traces 4 and 5 are each formed by stamping and bending a hard metal plate having sufficient hardness, such as bearing steel or case-hardened steel. ing. The first thrust trace 4 generally called an outer ring includes a flat and annular first thrust trace portion 7 and a cylinder provided in a state bent from the outer peripheral edge of the first thrust trace portion 7 to one side in the axial direction. The outer diameter side flange 8 is provided. Further, an outer diameter side locking portion 9 bent inward in the radial direction is provided at the front end edge of the outer diameter side flange 8. On the other hand, the second thrust trace 5 generally called an inner ring is a flat and annular second thrust trace portion 10 and is bent in one axial direction from the inner peripheral edge of the second thrust trace portion 10. A cylindrical inner diameter flange 11 is provided. Further, an inner diameter side locking portion 12 that is bent radially outward is provided at the tip edge of the inner diameter side flange 11.

  The inner diameter of the outer diameter side flange 8 is larger than the outer diameter of the retainer 3, and the outer diameter of the inner diameter side flange 11 is smaller than the inner diameter of the retainer 3. The cage 3 can be disposed between the thrust races 4 and 5 so as to freely rotate. The diameter of the inscribed circle of the outer diameter side locking portion 9 is slightly smaller than the outer diameter of the cage 3, and the diameter of the circumscribed circle of the inner diameter side locking portion 12 is the cage 3. It is slightly larger than the inner diameter. Then, while the flanges 8 and 11 are elastically deformed, the cage 3 holding the rollers 2 and the thrust races 4 and 5 are combined, and after the combination, the members 3, 4, and 5 It is relatively free to rotate and is not inadvertently separated. In the illustrated example, it is considered that the first thrust trace 4 is assembled to a member made of an iron-based alloy having high hardness, and the second thrust trace 5 is assembled to a member made of an aluminum-based alloy having low hardness. doing. For this reason, the thickness dimension of the second thrust trace 5 is made larger than the thickness dimension of the first thrust trace 4.

  The thrust roller bearing 1 with a race configured as described above has a holding portion 14 in which an outer diameter side flange 8 formed on the outer peripheral edge of the first thrust trace 4 is formed in a casing 13 as shown in FIG. Attached to a rotating part where a thrust load is generated while being fitted inside. Further, the second thrust trace 5 is brought into contact with the end surface of the mating member 15. In this state, the mating member 15 is rotatably supported with respect to the casing 13. The thrust load applied between the mating member 15 and the casing 13 is supported by the thrust bearing 1 with a race.

The above-described thrust bearing with a race 1 is required to have the following functions (1) to (4) arranged side by side as high as possible.
(1) The cage 3 and the two thrust traces 4 and 5 should not be inadvertently separated.
This function is achieved by separating each of the members 3, 4, and 5 until the thrust bearing 1 with race is transported from the bearing manufacturing plant to an assembly plant such as a transmission and assembled to a predetermined part. This is necessary to prevent the original performance of the thrust bearing 1 from being obtained and the assembly work of the transmission and the like from being troublesome.
(2) During operation of a transmission or the like, a flow rate of lubricating oil (lubricating oil flow rate) flowing through the internal space where the retainer 3 and the rollers 2 are installed can be secured between the thrust races 4 and 5. Thing.
This function ensures the strength of the oil film formed at the rolling contact portion between the rolling surface of each roller 2 and the first and second race portions 7 and 10 during operation of the transmission and the like. Necessary for effective cooling of the rolling contact.
(3) Even when the centers of rotation of the two thrust traces 4 and 5 are slightly deviated (the two thrust traces 4 and 5 are slightly eccentric), the relative position of the cage 3 with respect to the two thrust traces 4 and 5 That rotation is guaranteed.
This function ensures the function of the thrust bearing with race 1 even when the rotational centers of the thrust races 4 and 5 are slightly deviated due to manufacturing errors, assembly errors, etc. of the thrust bearing with race 1 and transmission. It is necessary for this purpose.
(4) The thrust roller bearing with race 1 can be assembled only in a predetermined direction with respect to the casing 13 or the like (it cannot be assembled in the reverse direction).
This function prevents the raceway thrust roller bearing 1 from being damaged, such as seizure, by assembling the thrust roller bearing 1 with race in the opposite direction to block the lubricating oil flow path. It is necessary for this purpose.

In the case of the conventional structure, it is difficult to align the functions shown in (1) to (4) above at a high level, which is disadvantageous for improving the performance of various mechanical devices incorporating a thrust bearing with a race such as a transmission. there were. Hereinafter, this point will be described.
In order to make the functions of (1) and (2) compatible at a high level, while increasing the engagement margin between the outer diameter side and inner diameter side locking portions 9 and 12 and the peripheral edge portion of the cage 3, It is necessary to widen the gaps existing between the outer and inner flanges 8 and 11 and the outer and inner peripheral surfaces of the cage 3. However, if the assemblability of the both thrust traces 4, 5 and the cage 3 is taken into consideration, the engagement allowance cannot be excessively increased. For example, when the cage 3 and the first thrust trace 4 are combined, as shown in FIG. 9 (A) → (B) → (C), the outer diameter side flange 8 is moved radially outward. The outer peripheral edge of the retainer 3 is moved over the outer diameter side engaging portion 9 while being elastically deformed. This operation becomes difficult if the protrusion amount δ of the outer diameter side locking portion 9 from the inner peripheral surface of the outer diameter side flange 8 is too large.

  Conventionally, the outer-diameter side locking portion 9 has a so-called full-curl structure in which the tip edge of the outer-diameter side flange 8 is bent radially inward over the entire circumference, and intermittently in the circumferential direction. There is a so-called partial curl structure in which a plurality of existing locations are bent inward in the radial direction. In the case of the full curl structure, the outer diameter of the retainer 3 is made smaller than the inner diameter of the outer diameter side flange 8 instead of making the protrusion amount δ considerably small or securing the protrusion amount δ. However, the cage 3 cannot be incorporated inside the outer diameter side flange 8 unless it is made considerably small. However, making the outer diameter of the retainer 3 much smaller than the inner diameter of the outer diameter side flange 8 ensures the positioning of the retainer 3 in the radial direction with respect to the first thrust trace 4 (this retainer). 3), which is not preferable from the surface. For this reason, when the full curl structure is employed, it is necessary to reduce the protrusion amount δ. In the roller bearing 1 with a race whose outer diameter side flange is 40 to 120 mm and whose inner diameter side flange is about 30 to 80 mm, the outer diameter side locking portion 9 has a full curl structure. In this case, if the protrusion amount δ is increased beyond 0.4 mm, it becomes difficult to incorporate the cage 3 inside the outer diameter side flange 8.

  On the other hand, if the partial curl structure is adopted, the amount of elastic deformation of the outer diameter side flange 8 when the retainer 3 is incorporated inside the outer diameter side flange 8 is increased (range of elastic deformation). Can be widely). Therefore, even if the protrusion amount δ of the outer diameter side locking portion 9 is increased and the difference between the outer diameter of the retainer 3 and the inner diameter of the outer diameter side flange 8 is reduced to some extent, this holding The vessel 3 can be assembled inside the outer diameter side flange 8 without any particular trouble. And as described in FIGS. 3-4 of patent document 2, while forming the outer-diameter side latching | locking part of a partial curl type in the circumferential direction several places of the front-end edge of an outer diameter side flange, this outer diameter side flange Among them, if the height dimension in the axial direction of the portion between the outer diameter side locking portions adjacent in the circumferential direction is reduced, the cage and the rollers are moved between the first and second thrust traces. The opening area on the outer diameter side of the installed internal space can be widened to ensure the lubricating oil flow rate, and the functions (1) and (2) can be obtained.

  However, the functions (3) and (4) cannot be obtained even by the structure described in FIGS. For example, in order to obtain the function (3), the relative displacement in the radial direction between the first and second thrust traces 4 and 5 constituting the thrust roller bearing 1 with race is to some extent. It must be an acceptable structure (not excessively but moderately). That is, both the thrust traces 4 and 5 rotate together with these members while being supported by a pair of members (for example, the casing 13 and the counterpart member 15) that rotate relative to each other. Therefore, if the rotational centers of these two members are displaced in the radial direction, the two thrust traces 4 and 5 swing around each other. When the radius (the amount of eccentricity) of the swinging motion is increased, as shown in FIG. 10, a part of the retainer 3 is moved to the inner peripheral surface of the outer diameter side flange 8 and the outer periphery of the inner diameter side flange 11. It is strongly clamped between the surfaces (causing “clamping” of the cage). As a result, a large radial load is applied to a part of the cage 3, and the cage 3 is likely to be damaged such as a crack or a crack. Further, the cage 3 does not rotate, and the rotation and rotation of the rollers 2 become impossible. The rolling surfaces of the rollers 2, the first of the first and second race portions 7 and 10, The second thrust thrust surfaces 17 and 20 rub against each other (sliding contact), and the thrust roller bearing 1 with the race has contact portions between the thrust thrust surfaces 17 and 20 and the rolling surfaces of the rollers 2. Serious damage such as seizure and breakage of the cage 3 occurs.

  In the case of the thrust roller bearing with race 1 in which the outer diameter of the outer diameter side flange 8 is 40 to 120 mm and the inner diameter of the inner diameter side flange 11 is about 30 to 80 mm, the outer diameter side locking portion is intended. When a full-curl type is adopted as 9 and the inner diameter side of the outer diameter side locking portion 9 is allowed to pass through the cage 3, the radial protrusion amount of the outer diameter side locking portion 9 is as described above. Must be suppressed to about 0.4 mm. Under this condition, the internal clearance of the thrust roller bearing with race 1 is limited to about 0.6 to 1.6 mm, and the radial shift (the radius of the whirling motion) of the rotation center of the two members is 0.5 mm. If exceeded, the possibility of occurrence of damage as described above increases. The patent document 2 does not describe a technique for preventing such damage.

  Further, when the thrust bearing with race 1 is assembled between the casing 13 and the mating member 15, if the assembly direction is wrong, durability is impaired due to poor lubrication, etc. Cannot be demonstrated. In other words, the thrust roller bearing with race 1 can be assembled to the casing 13 in the direction opposite to the normal state shown in FIG. However, when assembled in an irregular state, the first thrust trace 4 closes the gap 16 between the casing 13 and the mating member 15, and lubricating oil circulates inside the race roller bearing 1. Disturb things.

As a structure for preventing such reverse inconvenience, for example, in FIGS. 11 to 12 of Patent Document 3, the outer diameter of the second thrust trace portion of the second thrust trace is defined as the outer diameter of the first thrust trace. A structure that is larger than the outer diameter of the radial flange is described. According to such a structure, since the second thrust trace cannot be inserted into the holding portion of the casing, it is possible to prevent the second thrust trace from being assembled to the holding portion of the casing. That is, since only the first thrust trace that should be internally fitted can be assembled to the holding portion, the reverse assembly can be prevented. However, in the case of the conventional structure shown in FIGS. 11 to 12 of Patent Document 3, the outer peripheral edge of the second thrust trace portion is more radially outward than the outer peripheral surface of the outer flange. Since the protruding portion closes a considerable portion of the outer diameter side opening of the inner space of the thrust roller bearing with race and reduces the flow rate of the lubricating oil, the function (2) is impaired.
As can be seen from the above description, in the case of the conventional structure, it is difficult to align the functions shown in (1) to (4) in a high dimension.

Japanese Patent Laying-Open No. 2005-164023 JP 2008-039031 A JP 2004-028342 A

  In view of the circumstances as described above, the present invention increases the tolerance for the eccentricity of a pair of members that rotate relative to each other while ensuring the function of preventing separation between the cage and the pair of thrust traces. The invention was invented to realize a structure that has good handling properties and can secure a stable operating state even under severe use conditions by increasing the amount of lubricating oil distributed in the system.

The thrust roller bearing with race of the present invention includes a cage, a plurality of rollers, and both first and second thrust races.
Of these, the cage is in the shape of a ring, and is provided with pockets that are long in the radial direction at a plurality of locations in the circumferential direction.
The rollers are provided in the pockets so as to freely roll.
Further, both the thrust traces are combined in a non-separable manner so as to be relatively rotatable with respect to the cage, and both are formed by bending a hard metal plate.
Of these, the first thrust trace includes a flat and annular first thrust trace portion, and a cylindrical outer diameter side flange provided in a state bent from the outer peripheral edge of the first thrust trace portion to one axial direction. In addition, an outer-diameter side locking portion provided in a state of projecting inwardly in the radial direction from the distal end edge of the outer diameter side flange is provided at a plurality of positions in the circumferential direction at a part of the outer edge side flange. Further, the height dimension in the axial direction of the outer diameter side flange is made smaller at the portion where the outer diameter side locking portion is not provided than at the portion where the outer diameter side locking portion is also provided. Furthermore, the outer diameter of the outer diameter side flange is 40 to 120 mm.
On the other hand, the second thrust trace is a flat and annular second thrust trace portion, a cylindrical inner flange provided in a state bent from the inner peripheral edge of the second thrust trace portion to one side in the axial direction, A part of the front end edge of the inner diameter side flange is provided at a plurality of positions in the circumferential direction with inner diameter side engaging portions provided in a state of projecting radially outward from the front end edge of the inner diameter side flange. The inner diameter side flange has an inner diameter of 30 to 80 mm.

  In particular, in the thrust roller bearing with race of the present invention, the internal clearance is 1 to 2 mm. The internal gap is a dimension in which both the thrust traces can be relatively displaced in the radial direction without elastic deformation of each member, and it is assumed that both the flange and the cage are arranged concentrically. These are the sums of the radial dimensions of the annular gaps respectively existing between the inner peripheral surface of the outer diameter side flange and the outer peripheral surface of the inner diameter side flange and the inner and outer peripheral surfaces of the cage.

  When implementing the present invention as described above, preferably, as in the invention described in claim 2, the retainer is formed into a hollow ring shape by combining the first and second retainer elements. And Of these two cage elements, the first cage element disposed on the side of the first thrust trace portion is bent at right angles in the same direction with respect to the axial direction from the inner and outer peripheral edges of the annular flat plate portion. The first inner diameter side and the first outer diameter side both fitting cylindrical parts are formed. On the other hand, the second cage element arranged on the second thrust trace part side is in the same direction with respect to the axial direction from the inner and outer peripheral edges of the annular flat plate part, and the first inner diameter The second inner diameter side and the second outer diameter side both fitting cylindrical part bent at a right angle in the opposite direction to the side and first outer diameter side fitting cylindrical parts are formed. The first inner diameter side fitting cylindrical portion is fitted into the second inner diameter side fitting cylindrical portion, and the first outer diameter side fitting cylindrical portion is externally attached to the second outer diameter side fitting cylindrical portion. The two cage elements are combined with each other by fitting. Further, the diameter of the second outer diameter side fitting cylindrical portion is made larger at the front half portion farther from the second flat plate portion than the base half portion near the second flat plate portion, and the first outer diameter side The fitting cylindrical portion is fitted on the second outer diameter side fitting cylindrical portion only at the tip half portion.

Further, when the present invention as described above is carried out, preferably, as in the invention described in claim 3, the second thrust trace is divided into a ring-shaped second thrust trace portion (thrust trace main body) and the second thrust trace portion. It is assumed that at least one projecting piece provided in a state of projecting radially outward from a part of the outer peripheral edge of the second thrust trace portion is provided. The outer diameter of the second thrust trace portion is smaller than the inner diameter of the outer diameter side flange, and the diameter of the circumscribed circle of the second thrust trace including the projecting piece is smaller than the outer diameter of the outer diameter side flange. Enlarge.
When the invention described in claim 3 is carried out, more preferably, as in the invention described in claim 4, the thickness dimension of the projecting piece is set to the thickness dimension of the second thrust trace portion. Smaller than. A stepped portion is present at the boundary between one side of the projecting piece that faces the leading edge of the outer diameter flange and the race surface that causes the rollers to roll in contact with the second thrust trace portion. Let
When carrying out the invention described in claim 4, more preferably, as in the invention described in claim 5, the protruding pieces are disposed at a plurality of locations on the outer peripheral edge of the second thrust trace portion. Provide at equal intervals in the circumferential direction.

  According to the thrust roller bearing with race of the present invention configured as described above, the functions shown in the above (1) to (4) can be arranged in a high dimension. Specifically, while ensuring the function of preventing separation between the cage and the pair of thrust traces, the tolerance for the eccentricity of the pair of relatively rotating members is increased, and the amount of lubricating oil to be circulated inside is increased. By increasing the number, the handleability is good and a stable operation state can be secured even under severe use conditions.

Among these, the separation preventing function of (1) described above is based on the engagement between the outer diameter side locking portion and the outer peripheral edge of the cage. The retainer and the second thrust trace can be combined in a non-separable manner by engaging with the inner peripheral edge of the container.
Thus, in order to combine the two thrust traces and the retainer in a non-separable manner, the outer diameter side and the inner diameter side locking portions respectively provided at the front end edges of both the outer diameter side and inner diameter side flanges, Are also formed intermittently at a plurality of locations in the circumferential direction of the leading edge of each flange. Therefore, even if the protrusion amount in the radial direction of each locking portion is increased, both the thrust traces and the cage can be combined. And since the protrusion amount in the radial direction of each of the locking portions can be increased, the difference between the inner diameter of the outer diameter side flange and the outer diameter of the cage, and the outer diameter of the inner diameter side flange and the cage Even if the difference from the inner diameter is increased to some extent, it is possible to reliably perform the function of preventing separation between the retainer and both the thrust traces. As a result, a relatively large value of 1 to 2 mm can be adopted as the internal clearance of the thrust roller bearing with race.

  By adopting such a large value as the internal gap, it is possible to ensure the relative rotation of the cage with respect to both thrust traces even when both thrust traces have a slight swinging motion. That is, because the internal gap is large, even if the interval between the inner peripheral surface of the outer diameter side flange and the outer peripheral surface of the inner diameter side flange is narrowed in a part in the circumferential direction based on the swinging motion. The interval between the portions can be kept larger than the radial width of the cage. Accordingly, a part of the cage in the circumferential direction is not strongly held between the inner peripheral surface of the outer diameter side flange and the outer peripheral surface of the inner diameter side flange. As a result, even when the centers of rotation of both thrust traces are slightly deviated, the relative rotation of the cage with respect to both thrust traces can be ensured and the function (3) can be achieved.

  Further, by taking a relatively large value as the internal gap, and by reducing the height dimension in the axial direction of the portion of the outer diameter side flange not provided with the outer diameter side locking portion. The amount of lubricating oil flowing through the internal space can be secured. That is, by reducing the height of the outer diameter side flange in part, the lubricating oil can easily pass through the outer diameter flange in the radial direction. Further, by enlarging the internal gap, the lubricating oil can easily pass between the inner and outer peripheral edges of the cage, the inner peripheral surface of the outer diameter side flange, and the outer peripheral surface of the inner diameter side flange. As a result, the lubricating oil flow rate of the thrust roller bearing with race can be ensured during operation, and the function (2) can be performed at a high level.

Further, as in the invention described in claim 2, the first outer diameter side fitting cylindrical portion formed on the outer peripheral edge of the first cage element constituting the cage is formed on the outer peripheral edge of the second cage element. The outer peripheral edge of the retainer and the outer diameter side latching portion are engaged with the second outer diameter side fitting cylindrical portion if only the first half of the second outer diameter side fitting cylindrical portion is externally fitted. It is possible to easily achieve both of ensuring the above and preventing friction between the outer peripheral edge of the cage and the outer diameter side locking portion.
Further, as in the inventions described in claims 3 to 5, by providing a projecting piece on the outer peripheral edge of the second thrust trace portion constituting the second thrust trace, a thrust roller bearing with a race is provided for the rotation support portion. Therefore, it is possible to reliably prevent the assembly in the reverse direction, and the function (4) can be achieved. Since the circumferential width of the projecting piece is limited, the projecting piece rarely obstructs the flow of the lubricating oil flowing through the inner space, and even if it has a reverse assembly preventing function, the (2) There is almost no loss of function. In particular, if the thickness dimension of the projecting piece is reduced as in the invention described in claim 4, the gap between one surface of the projecting piece and the leading edge of the outer diameter side flange is sufficiently widened. The extent to which this protruding piece hinders the flow of the lubricating oil can be further reduced.

The fragmentary sectional view which shows the 1st example of embodiment of this invention. The figure (a) seen from the lower part of Drawing 1, and the figure (b) seen from the diameter direction which show two examples of the shape of the 1st thrust trace. The figure seen from the upper part of FIG. 1 which shows two examples of the shape of a 2nd thrust trace. The fragmentary sectional view which shows the 2nd example of embodiment of this invention. Sectional drawing which shows the implementation condition of the test regarding durability at the time of driving | running | working eccentrically the 1st, 2nd both thrust traces. Sectional drawing which shows the implementation condition of the test regarding the distribution | circulation amount of lubricating oil. The fragmentary sectional view which shows an example of the thrust bearing with a race known conventionally. The fragmentary sectional view which shows an example of the assembly | attachment state of this thrust bearing with a race. The fragmentary sectional view which shows the process of combining a 1st thrust trace and the holder | retainer holding each roller in order. Sectional drawing which shows the state in which the holder | retainer was bitten between the outer diameter side flange and the inner diameter side flange based on the eccentric motion of both the first and second thrust races.

[First example of embodiment]
1 to 3 show a first example of an embodiment of the present invention corresponding to claims 1 and 3 to 5. The thrust roller bearing with race 1a of this example includes a cage 3, a plurality of rollers 2, and first and second thrust races 4a and 5a. Since the structure of the retainer 3 and each roller 2 is the same as that of the conventional structure shown in FIG. 7 described above, the same reference numerals are given to the same parts, and duplicate descriptions are omitted. In addition, the first and second thrust races 4a and 5a are formed by bending a hard metal, and the conventional structure is also provided in that the relative rotation with the cage 3 can be freely and non-separated. It is the same.

  Of the two thrust traces 4a and 5a, the first thrust trace 4a includes a first thrust trace portion 7a, an outer diameter side flange 8a, a plurality of {three in the structure of FIG. 2 (A), and (B). The structure shown includes six} outer diameter side locking portions 9a, 9a. Of these, the first thrust trace portion 7 a is flat and annular, and has one axial surface (the lower surface in FIG. 1) as the first thrust trace surface 17. Further, the outer diameter side flange 8a has a short cylindrical shape, and is substantially from the outer peripheral edge of the first thrust trace portion 7a to one axial direction side (lower side in FIG. 1) where the first thrust trace surface 17 exists. It is provided in a state bent at a right angle.

  Further, each of the outer diameter side locking portions 9a, 9a is provided at a plurality of positions at equal intervals in the circumferential direction at a part of the end edge of the outer diameter side flange 8a (three positions in the structure of FIG. In the structure shown in B), six locations} are directed inward in the radial direction and bent by less than 90 degrees so as to protrude radially inward from the leading edge of the outer diameter side flange 8a. The diameters of the inscribed circles of the outer diameter side engaging portions 9a, 9a are slightly smaller than the outer diameter of the cage 3 (for example, about 1 to 2 mm).

  Furthermore, notch portions 18 and 18 are formed in a portion between the outer diameter side locking portions 9a and 9a adjacent to each other in the circumferential direction at the remaining portion of the front end edge of the outer diameter side flange 8a. Then, based on the presence of the notches 18 and 18, the height dimension in the axial direction of the outer diameter side flange 8a is also provided in the portion where the outer diameter side locking portions 9a and 9a are not provided. It is smaller than the part. The shape of each notch 18, 18 is not particularly limited. It may be trapezoidal as shown in FIGS. 2A and 2B, or may be arcuate as shown in FIGS. 2B and 2B. The size of the first thrust trace 4a as described above is 40 to 120 mm as the outer diameter of the outer diameter side flange 8a.

  On the other hand, the second thrust trace 5a includes a second thrust trace portion 10a, an inner diameter side flange 11a, a plurality of (four in the illustrated example) inner diameter side locking portions 12a, 12a, and a plurality of { A) has three projecting pieces 19 and 19 in the structure, and two in the structure shown in (B). Of these, the second thrust trace portion 10a is flat and annular, and has one axial surface (the upper surface in FIG. 1) as the second thrust trace surface 20. Further, the inner diameter side flange 11a has a short cylindrical shape, and is substantially perpendicular to the one side in the axial direction (upper side in FIG. 1) where the second thrust trace surface 20 exists from the inner peripheral edge of the second thrust trace portion 10a. It is provided in a bent state.

  Further, each of the inner diameter side locking portions 12a, 12a has a plurality of circumferential positions (four positions in the illustrated example) directed radially outward at a part of the tip edge of the inner diameter side flange 11a. The flange 11a is provided so as to protrude radially outward from the front end edge of the flange 11a. In the case of this example, the inner diameter side locking portions 12a, 12a are bent so that the distal end edge of the inner diameter side flange 11a faces radially outward and the shape viewed from the axial direction is substantially V-shaped. Become. In addition, about the shape etc. of each said inner diameter side latching | locking part 12a, 12a, it is the same as that of "the latching | locking part 7a, 7a" described in FIGS. Since it is a widely known shape, detailed description is omitted. Also with respect to the leading edge of the inner diameter side flange 11a, notches 21 and 21 are formed in a portion between the inner diameter side locking portions 12a and 12a adjacent to each other in the circumferential direction, and the shaft of the inner diameter side flange 11a is formed. The height dimension with respect to the direction is made smaller at the portion where the inner diameter side locking portions 12a, 12a are not provided than at the portion where the same is provided.

  Further, each of the projecting pieces 19, 19 is provided at a plurality of circumferentially equidistant positions among the outer peripheral edges of the second thrust trace portion 10a (three positions in the structure of FIG. 3A, shown in FIG. 3B). In the above structure, it is formed at two locations} so as to protrude radially outward from the outer peripheral edge of the second thrust trace portion 10a. The shape of each projecting piece 19, 19 is not particularly limited. It may be a semicircular shape as shown in FIG. 3A or a rectangular shape as shown in FIG. The thickness dimension t of each of the projecting pieces 19, 19 is smaller than the thickness dimension T of the second thrust trace portion 10a (t <T). However, on the side opposite to the second thrust trace surface 20 (the lower side in FIG. 1), the second thrust trace portion 10a and the protrusions 19 and 19 are on the same plane. Accordingly, on the second thrust trace surface 20 side, a height dimension h (= T−) is formed at a boundary portion between the one surface (the upper surface in FIG. 1) of each of the projecting pieces 19 and 19 and the second thrust trace surface 20. There is a step 22 having t). The size of the second thrust trace 5a having such a shape is about 30 to 80 mm in terms of the inner diameter of the inner diameter side flange. Further, the outer diameter of the second thrust trace portion 10a is larger than the diameter of the circumscribed circle of the rollers 2, and smaller than the inner diameter of the outer diameter side flange 8a. The diameter of the circumscribed circle of each of the projecting pieces 19, 19 is larger than the outer diameter of the outer diameter side flange 8a.

Furthermore, the thrust roller bearing with race 1a of this example appropriately regulates the outer diameter and inner diameter of the cage 3, the inner diameter of the outer diameter side flange 8a, and the outer diameter of the inner diameter side flange 11a. The size of the internal gap is set to 1 to 2 mm. The internal clearance means that the first and second thrust traces 4a and 5a of the members 3, 4a and 5a constituting the thrust roller bearing 1a with race are not relatively deformed in the radial direction. It is a dimension that can be displaced. These thrust traces 4a and 5a are eccentric, and as shown in the upper part of FIG. 10 described above, the circumferential direction of the retainer 3 is between the peripheral surfaces of the outer and inner diameter side flanges 8a and 11a. When a part is sandwiched, on the opposite side in the radial direction, as shown in the lower part of FIG. 10 described above, both the inner and outer peripheral surfaces of the cage 3, the outer peripheral surface of the inner diameter side flange 11 (11a), and the outer diameter side A gap is interposed between the inner peripheral surface of the flange 8 (8a). When the radial dimensions of both the gaps are C ₁ and C ₂ , the internal gap is (C ₁ + C ₂ ) / 2. In other words, assuming that the outer diameter side and inner diameter side flanges 8a and 11a and the retainer 3 are arranged concentrically, the inner peripheral surface of the outer diameter side flange 8a and the retainer 3 annular gap radial dimension _{c 2 (= C 2/2} ) between the outer peripheral surface, c _{1 (=} C between the outer peripheral surface and the inner peripheral surface of the retainer 3 of the inner diameter side flange 11a _1/2) of the annular gap, a condition mediated respectively. The value of the internal gap is represented by the sum (c ₁ + c ₂ ) of the radial dimensions of both annular gaps.

  Since the thrust roller bearing with race 1a according to this example is configured as described above, both the thrust and the first and second thrust traces 4a and 5a are secured while ensuring the function of preventing separation between the cage 3 and the first and second thrust traces 4a and 5a. The tolerance for the eccentricity of the pair of members that rotate relative to each other while supporting the races 4a and 5a can be increased, and the amount of lubricating oil to be circulated inside can be increased. As a result, it is possible to realize the thrust roller bearing with race 1a that has good handleability and that can ensure a stable operation state even under severe use conditions.

  First, the function of preventing the separation while allowing the relative rotation of the members 3, 4 a, 5 a is based on the engagement between the outer diameter side locking portions 9 a, 9 a and the outer peripheral edge of the cage 3. The retainer 3 and the first thrust trace 4a are brought into engagement with the inner diameter side locking portions 12a and 12a and the inner peripheral edge of the retainer 3, and the retainer 3 and the second thrust trace 5a. Can be achieved by combining them in a non-separable manner. In the case of the thrust roller bearing with race 1a of this example, each of the outer diameter side and inner diameter side engaging portions 9a, 12a is a circle at the tip edge of both the outer diameter side and inner diameter side flanges 8a, 11a. It is intermittently formed at a plurality of locations in the circumferential direction. Therefore, even if the protruding amount in the radial direction of each of the locking portions 9a and 12a is increased to some extent, the both thrust traces 4a and 5a and the cage 3 can be combined.

  That is, each of the outer diameter side and inner diameter side flanges 8a and 11a provided with the outer diameter side and inner diameter side engaging portions 9a and 12a intermittently at a plurality of positions in the circumferential direction of the respective leading edges. The bending rigidity is lower than that of a flange provided with a locking portion (full curl type) over the entire circumference, and the outer peripheral edge portion or the inner peripheral edge portion of the cage 3 can be easily passed. For this reason, as described above, the protruding amount in the radial direction of each of the locking portions 9a and 12a can be increased. And since the protrusion amount of each of the locking portions 9a and 12a can be increased, the difference between the inner diameter of the outer diameter side flange 8a and the outer diameter of the retainer 3, the outer diameter of the inner diameter side flange 11a, and this Even if the difference from the inner diameter of the cage 3 is increased, the function of preventing separation between the cage 3 and the first and second thrust traces 4a and 5a can be performed reliably. As a result, a relatively large value such as 1 to 2 mm can be adopted as the internal clearance of the thrust roller bearing with race 1a.

  And the thrust roller bearing 1a with a race of this example employ | adopts a large value (1-2 mm) as mentioned above as said internal clearance, and said 1st, 2nd both thrust traces 4a, 5a have some. Even when a swinging motion (eccentric motion) is performed, the relative rotation of the cage 3 with respect to both the thrust traces 4a and 5a can be ensured. That is, since the internal gap is large, the distance between the inner peripheral surface of the outer diameter side flange 8a and the outer peripheral surface of the inner diameter side flange 11a, as shown in the upper part of FIG. However, even if it becomes narrow in a part in the circumferential direction, the interval between the parts can be kept larger than the radial width of the cage 3. Accordingly, a portion of the cage 3 in the circumferential direction is not strongly clamped between the inner peripheral surface of the outer diameter side flange 8a and the outer peripheral surface of the inner diameter side flange 11a. As a result, even when the rotation centers of the first and second thrust traces 4a and 5a are slightly deviated from each other, the relative rotation of the cage 3 with respect to both the thrust traces 4a and 5a can be ensured. For example, in the case of the conventional structure shown in FIG. 7 described above, if the deviation between the rotation centers exceeds 0.5 mm, as described above, the cage 3 is broken or the thrust trace surface and the rollers 2 roll. Damage such as seizure of the contact portion with the surface is likely to occur. On the other hand, in the case of the thrust roller bearing with race 1a of the present example, the internal gap can be increased, so that the above-mentioned even under severe use conditions such that the deviation between the rotation centers exceeds 0.6 mm. The occurrence of such damage can be prevented.

  In addition, a relatively large value (1 to 2 mm) can be taken as the internal gap, and the outer diameter side and inner diameter side engaging portions 9a and 12a of the outer diameter side and inner diameter side flanges 8a and 11a By forming the notches 18 and 21 in a portion not provided and reducing the height dimension in the axial direction of this portion, it is possible to secure the amount of lubricating oil flowing through the internal space. That is, by reducing the height dimension of both the outer diameter side and inner diameter side flanges 8a and 11a in part, the outer diameter side and inner diameter side both flanges 8a and 11a and the peripheral portion of the cage 3 are separated. The area of the opening in the internal space can be increased to about 2 to 10 times that of the conventional structure shown in FIG. Then, it is possible to smoothly flow the lubricating oil into the internal space and discharge the lubricating oil from the internal gap so that the lubricating oil can easily pass through the internal space in the radial direction. Further, by enlarging the internal gap, the lubricating oil is caused to cause an annular gap between the inner and outer peripheral edges of the cage 3 and the inner peripheral surface of the outer diameter side flange 8a and the outer peripheral surface of the inner diameter side flange 11a. Can be easily passed. As a result, the lubricating oil flow rate of the thrust roller bearing with race 1a can be sufficiently secured during operation, and the flow rate of the lubricating oil is increased by 20% or more, for example, about 40% compared to the conventional structure shown in FIG. This makes it possible to improve the reliability and durability of the thrust roller bearing with race 1a.

  Further, in the case of the thrust roller bearing with race 1a of this example, the projecting pieces 19, 19 are provided on the outer peripheral edge of the second thrust trace portion 10a constituting the second thrust trace 5a. The diameter of the circumscribed circle of each of the projecting pieces 19, 19 is larger than the outer diameter of the outer diameter side flange 8a. Therefore, for example, the first thrust trace 4a provided with the outer diameter side flange 8a can be fitted into the holding portion 14 of the casing 13 shown in FIG. 8, but the protrusions 19 and 19 are provided. The second thrust trace 5a cannot be fitted. For this reason, it can prevent reliably that the said thrust roller bearing 1a with a race is excessively assembled | attached to the said casing 13 which comprises a rotation support part.

  Further, since the circumferential widths of the projecting pieces 19 and 19 are limited, the projecting pieces 19 and 19 rarely obstruct the flow of the lubricating oil flowing through the inner space. Therefore, even if the reverse assembly prevention function is provided, the lubricating oil flow rate can be sufficiently secured. In addition, in the case of the thrust roller bearing with race 1a of this example, the thickness dimension t of each of the projecting pieces 19, 19 is set to the tip edge of the outer diameter side flange 8a. It is made small by denting the surface side that faces. For this reason, the clearance gap between the one side of each said protrusion 19 and 19 and the front-end edge of the said outer diameter side flange 8a is made wide enough, and these protrusions 19 and 19 prevent the flow of lubricating oil. Can be further reduced.

[Second Example of Embodiment]
FIG. 4 shows a second example of an embodiment of the present invention corresponding to claims 1 and 2. In the case of this example, by devising the structure of the retainer 3a, the outer peripheral edge of the retainer 3a and a plurality of outer diameter side locking portions 9a provided on the outer peripheral edge of the first thrust trace 4a. It is easy to achieve both the securing of the engagement allowance and the prevention of rubbing between the outer peripheral edge of the cage 3a and the outer diameter side locking portion 9a.

  The basic configuration itself of the cage 3a is the same as that of the first example of the above-described embodiment. By combining both the first and second cage elements 25 and 26, the whole has a hollow ring shape. Of these two cage elements 25 and 26, the first cage element 25 arranged on the first thrust trace portion 7a side of the first thrust trace 4a is composed of a first flat plate portion 27 and a first inner diameter side. A fitting cylindrical portion 28 and a first outer diameter side fitting cylindrical portion 29 are provided. Of these, the first flat plate portion 27 is in the shape of a ring, and has long rectangular first through holes 30 that are long in the radial direction, and are radially formed at a plurality of locations at equal intervals in the circumferential direction. The first inner diameter side and first outer diameter side fitting cylindrical portions 28 and 29 are bent at right angles in the same direction with respect to the axial direction from both inner and outer peripheral edges of the first flat plate portion 27. The second cage element 26 disposed on the second thrust trace portion 10b side of the second thrust trace 5b includes a second flat plate portion 31, a second inner diameter side fitting cylindrical portion 32, and a second outer portion. And a radial fitting cylindrical portion 33. Of these, the second flat plate portion 31 is in the shape of a ring, and at a plurality of equally spaced circumferential locations, each of which is a long rectangle extending in the radial direction, and the same number of second through holes 34 as the first through holes 30. It is formed radially. The second inner diameter side and the second outer diameter side fitting cylindrical portions 32, 33 are in the same direction with respect to the axial direction from the inner and outer peripheral edges of the second flat plate portion 31, and the first inner diameter side, The first outer diameter side fitting cylindrical portions 28 and 29 are bent at right angles to the opposite side. Further, the diameter of the second outer diameter side fitting cylindrical portion 33 is made larger at the front half portion 36 on the side farther from the second flat plate portion 31 than at the base half portion 35 near the second flat plate portion 31. The second outer diameter side fitting cylindrical portion 33 has a stepped cylindrical shape.

  The first and second cage elements 25 and 26 as described above are fitted into the second inner diameter side fitting cylindrical portion 32 by interference fitting the first inner diameter side fitting cylindrical portion 28, and the first The retainer elements 25 and 26 are combined with each other by fitting the outer diameter side fitting cylindrical portion 29 to the front half portion 36 of the second outer diameter side fitting cylindrical portion 33 by an interference fit. The container 3a is used. At this time, the first outer diameter side fitting cylindrical portion 29 is fitted on the second outer diameter side fitting cylindrical portion 33 only at the front half portion 36. For this purpose, the height (axial dimension) of the first outer diameter side fitting cylindrical portion 29 is set to be equal to or less than the height of the tip half portion 36. The combination work of both the cage elements 25 and 26 is the first and second through holes 30 formed in the first and second flat plate portions 27 and 31 of the both cage elements 25 and 26, respectively. The phase of 34 is adjusted, and the roller 2 is disposed between each of the through holes 30 and 34. The lengths (diameter direction dimensions) of the respective through holes 30 and 34 are larger than the lengths of the respective roller 2, and the widths (circumferential dimension) of the respective through holes 30 and 34 are larger than the outer diameters of the respective roller 2. small. Therefore, when the cage 3a is configured by combining the first and second cage elements 25 and 26, the rollers 2 are dropped between the first and second through holes 30 and 34. In a state where the movement is blocked, the roll is held freely. That is, the first and second through holes 30 and 34 are combined to form the pocket 6.

  According to the structure of this example configured as described above, the engagement margin between the outer peripheral edge of the retainer 3a and the plurality of outer diameter side locking portions 9a provided on the outer peripheral edge portion of the first thrust race 4a. Both securing and preventing friction between the outer peripheral edge of the retainer 3a and the outer diameter side engaging portion 9a can be achieved. That is, in the case of the structure of this example, since the height of the first outer diameter side fitting cylindrical portion 29 which is the maximum outer diameter portion of the cage 3a is reduced, the first outer diameter side The fitting cylindrical portion 29 and the outer diameter side locking portion 9a can be prevented from overlapping with respect to the radial direction. For this reason, during the operation of the thrust roller bearing with race 1c, it is possible to prevent the outer diameter side engaging portions 9a provided intermittently in the circumferential direction from rubbing against the outer peripheral edge of the cage 3a. It is possible to ensure smooth rotation of the cage 3a and to stabilize the operation state of the thrust roller bearing with race 1c.

  About the structure and effect | action of another part, since the protrusion 19 (refer FIG. 1, 3) is abbreviate | omitted, since it is substantially the same as the 1st example of embodiment mentioned above, it is the overlapping description. Is omitted. As for the structure of this example, as in the case of the first example of the above-described embodiment, the second thrust trace 5b is to be implemented together with the invention described in claims 3 to 5 in the claims. The projecting piece 19 can be provided on the outer peripheral edge of the second thrust trace portion 10b.

Tests conducted to confirm the effects of the present invention will be described with reference to Tables 1 and 2 and FIGS. Of these, Table 1 and FIG. 5 show the effect of the size of the internal clearance of the thrust roller bearing with race on the durability when the first and second thrust traces are operated eccentric to each other. Two types of tests (eccentricity test) and tests (load ON / OFF test) for determining the influence on the durability of the operation state in which the thrust load is applied and the state where the load is not applied alternately The conditions and results are shown. Conditions common to these two types of tests are as follows.
Outer diameter of thrust roller bearing with race: 85mm
Same inner diameter: 54mm
Similarly axial thickness (bearing width): 5.4mm
Test load (P / C): 0.4 (Fa = 12600N)
Rotational speed (1st thrust race side rotation): 6000 min ^-1
Lubrication condition: Oil bath immersed in the center of rotation by ATF Lubricating oil temperature: 120 ° C
In the eccentricity test, the central axes of the first and second thrust traces were shifted by 0.6 mm using the eccentric jig 23 shown in FIG.
Further, in the load ON / OFF test, the test load is applied to the thrust roller bearing 1b with a race through the thrust roller bearing 1b with a race, which is a test object, and another thrust bearing 24 every 2 seconds (one cycle). Added repeatedly (as 4 seconds). The first and second thrust traces were concentric with each other.

  The test is performed while measuring the vibration generated in the thrust roller bearing 1b with a race by a vibrometer. When this vibration exceeds a preset threshold, the life of the thrust roller bearing 1b with a race is reduced. The test was terminated at that point. In Table 1 below, “x” marks representing failures are shown along with the time until censoring. If the vibration does not increase until 60 hours (hr) elapses, the test is stopped at that point, the race thrust roller bearing 1b is disassembled, the cage is damaged, the thrust trace surface Observe the presence or absence of damage such as flaking. If there is any damage, mark “x” to indicate failure, and mark “○” to indicate pass if there is no damage. These are shown in Table 1, respectively.

In Table 1, Examples 1 to 6 all have the size of the internal gap within the range of 1 to 2 mm, and even when operated under a large eccentric amount of 0.6 mm, In either case, no damage such as breakage of the cage or flaking occurred even when the calculated life reached 60 hours (effect by setting the internal gap to 1 mm or more). Also, in the load ON / OFF test, when the thrust load is released (when the load is OFF), the cage drops due to its own weight, and then the thrust roller bearing with race rotates with the load turned ON. Part of the circumferential direction of the cage was caught between the inner peripheral surface of the outer diameter side flange and the outer peripheral surface of the inner diameter side flange. However, even in this case, the wear of the cage is slight, and even if the calculated life reaches 60 hours, no particular damage will occur in any part of the thrust roller bearing with race. (Effect by suppressing the internal gap to 2 mm or less).
On the other hand, in the case of Comparative Examples 1 to 7 in which the size of the internal gap is out of the range of the present invention (1 to 2 mm), either or both of the eccentricity test and the load ON / OFF test are rejected. became. That is, in Comparative Examples 1, 2, 4, 6, and 7 in which the internal gap was small, the cage was caught in any of the tests described above. In some cases, the test could be continued until 60 hours had passed. However, when the thrust roller bearing with race was disassembled and each part was examined, damage such as cracks or flaking had occurred.
From the tests shown in Table 1 as described above, it was confirmed that a thrust roller bearing with race having excellent durability can be realized by restricting the internal gap to 1 to 2 mm.

Next, a description will be given of a test conducted in order to know the influence of the difference in structure of the thrust roller bearing with race on the lubricating oil flow rate of the thrust roller bearing with race. The test conditions are as follows.
Outer diameter of thrust bearing with race: 85mm
Same inner diameter: 54mm
Similarly axial thickness (bearing width): 5.4mm
Test load (P / C): 0.05 (Fa = 12600N)
Rotational speed (second thrust race side ^{rotation): 500min -1, 3000min -1,} 3 -stage lubrication conditions of 5000 min ^-1: supplied from the inner diameter side ATF at a pressure of 5kPa lubricating oil temperature: 100 ° C.
First Thrust Trace Thickness: 0.8mm
Second thrust trace thickness: 1.6mm
The results of tests conducted under such conditions are shown in Table 2 below. In addition, the structure of Examples 1-6 and Comparative Examples 1-7 respond | corresponds with Table 1 and Table 2, respectively (it is the same specification).

As is apparent from the description in Table 2 showing the results of the tests performed under the conditions as described above, the thrust roller bearings with races of Examples 1 to 6 belonging to the technical scope of the present invention all have rotational speeds. Regardless, the amount of lubricating oil passing through the inner space can be secured twice or more as compared with the thrust roller bearings with races of Comparative Examples 1 to 7 that deviate from the technical scope of the present invention.
As described above, as apparent from the results of the three types of tests shown in Tables 1 and 2, according to the thrust roller bearing with race belonging to the technical scope of the present invention, the handleability is good, It is possible to realize a structure that can ensure a stable operating state even under severe use conditions.

  The structure of Comparative Example 1 is provided with a full-curl outer diameter side locking portion, but the internal clearance is 0.8 mm, the amount of pinching is 0.2 mm, and the test is completed after 60 hours. However, when the inside was confirmed, the cage was cracked. In the load ON / OFF test, no abnormality occurred even after 60 hours. However, it was found that the lubricating oil flow rate was small because the opening area was small, and it became difficult to ensure sufficient durability when the usage conditions became severe.

  Further, regarding Comparative Examples 2 to 5, a plurality of outer diameter side engaging portions are intermittently formed in the circumferential direction in the distal end edge portion of the outer diameter side flange, and the adjacent outer diameter side in the circumferential direction. Notches were formed between the locking portions, and the internal gap was set to 0.8 mm or 2.3 mm, and the eccentricity test passed as far as Comparative Examples 3 and 5 were concerned. However, in these Comparative Examples 3 and 5, the internal gap was excessive, and in the load ON / OFF test, the cage was broken during the OFF because of the large amount of the cage dropped at OFF. In Comparative Examples 2 and 4, the cage was damaged in the eccentric test due to wear of the outer peripheral edge of the cage. Regarding the lubricating oil flow rate, in the case of Comparative Examples 2 to 7, it increased compared to Comparative Example 1, but was still small compared to Examples 1 to 6. In Examples 1 to 6, Examples 2, 3, 5, and 6 in which the protrusions for preventing reverse assembly are thinned (provided with steps) are not particularly thinned to Examples 1 and 4. In comparison, the lubricating oil flow rate could be increased further.

  Further, as described above, with respect to Comparative Examples 6 and 7, for example, as shown in FIGS. 7, it is difficult to provide an outer diameter side latching portion having a large protrusion at the distal end edge of the outer diameter side flange constituting the thin first thrust trace, and therefore it is possible to secure an internal gap. difficult. That is, in Comparative Examples 6 and 7, the internal gaps were as small as 0.6 mm and 0.4 mm, respectively, and in the eccentric test, wear occurred on the outer peripheral edge of the cage and the cage broke. In the load ON / OFF test, the cage breakage occurred midway. In addition, it is easy to ensure a large protruding amount at the tip edge of the inner diameter side flange constituting the relatively thick second thrust trace, even with the normal tab structure as described above. Therefore, also for the first example of the embodiment of the present invention shown in FIGS. 1 and 3, the normal tabs as described above are used as the inner diameter side locking portions 12a and 12a formed at the tip edge of the inner diameter side flange 11a. The structure is adopted. Regarding the lubricating oil flow rate, the same tendency as in Comparative Examples 1 to 5 was shown in Comparative Examples 6 and 7.

The thrust roller bearing with a race of the present invention is not limited to a transmission of an automobile, but can be used for a rotation support portion of various rotary machines such as agricultural machinery, construction machinery, steel machinery, and engine auxiliary machinery such as a compressor.
In the illustrated embodiment, the cage used in practicing the present invention adopts a structure in which a pair of cage elements each formed by bending a metal plate are combined in a hollow ring shape. Yes. As the metal plate constituting both the cage elements, for example, a carbon steel plate having a thickness of about 0.4 mm (for example, SPCC material) and having a surface hardness of Hv400 to Hv850 can be used. However, it is also possible to use a metal plate bent into a crank shape in cross section to form a ring shape as a whole, or a cage made of synthetic resin (for example, PA66, PA46, PPS, etc.).

  Regardless of which cage is used, the axial thickness of the cage should be 80% or less of the diameter of each roller so that both axial sides of the cage and the first and second thrust traces can be used. It is preferable to ensure the thickness of the annular space between the surface and the lubricating oil flow rate. However, if the axial thickness of the cage is less than 50% of the diameter of each roller, it becomes difficult to engage the inner surface of each pocket formed in the cage and the rolling surface of each roller ( It becomes difficult to regulate the axial position of this cage by each roller, and if it is attempted to regulate it forcibly, the inner surface of each pocket and the rolling surface of each of these rollers rub against each other strongly) There is a high possibility that rolling will be hindered. Therefore, it is preferable that the thickness of the cage in the axial direction be within a range of 50 to 80% of the diameter of each of these rollers.

Further, the thickness dimension of the first thrust trace is not limited to 0.8 mm as described above. For example, this first thrust trace is made of a baked material having a carbon content (C%) of 0.5 to 1.0% by weight, such as SK85, or a carburized material such as SCM415 (C% of material = 0. 1 to 0.5% by weight), partial curl processing is possible when the thickness of the first thrust trace is in the range of 0.6 to 2.0 mm. In the case of full curl processing, if the thickness exceeds 1.0 mm, it is difficult to process the outer diameter side locking piece by press processing that can be performed at low cost.
Regarding the second thrust trace, the materials that can be used are the same as those of the first thrust trace described above. Although the thickness has been described above for the case of 2.0 mm, it can be implemented in the range of 0.6 to 5.0 mm.

1, 1a, 1b, 1c Race thrust roller bearing 2 Roller 3, 3a Cage 4, 4a First thrust trace 5, 5a, 5b Second thrust trace 6 Pocket 7, 7a First thrust trace portion 8, 8a Outer diameter Side flange 9, 9a Outer diameter side locking portion 10, 10a, 10b Second thrust trace portion 11, 11a Inner diameter side flange 12, 12a Inner diameter side locking portion 13 Casing 14 Holding portion 15 Counter member 16 Clearance 17 First thrust trace Surface 18 Notched portion 19 Projection piece 20 Second thrust trace surface 21 Notched portion 22 Stepped portion 23 Eccentric jig 24 Thrust bearing 25 First cage element 26 Second cage element 27 First flat plate portion 28 First inner diameter side Fitting cylindrical portion 29 First outer diameter side fitting cylindrical portion 30 First through hole 31 Second flat plate portion 32 Second inner diameter side fitting cylindrical portion 33 Second outer diameter side fitting Cylindrical portion 34 second through hole 35 Motohan unit 36 destination halves

Claims (5)

  A ring-shaped cage with multiple radially extending pockets at multiple locations in the circumferential direction, a plurality of rollers that can roll in each of these pockets, and relative rotation with this cage The first and second thrust traces are combined in a non-separable manner, and the first thrust trace is formed by bending a hard metal plate, and is a flat and annular first thrust trace portion. And a cylindrical outer diameter flange provided in a state bent from the outer peripheral edge of the first thrust trace portion to one side in the axial direction, and a part of the tip edge of the outer diameter side flange at a plurality of locations in the circumferential direction. And an outer diameter side locking portion provided in a state of projecting radially inward from the leading edge of the outer diameter side flange, and the height dimension of the outer diameter side flange in the axial direction is At the part where the outer diameter side locking part is not provided Similarly, the outer diameter side flange is smaller than the provided part, and the outer diameter side flange has an outer diameter of 40 to 120 mm. The second thrust trace is formed by bending a hard metal plate, and is a flat and annular second thrust. A cylindrical inner diameter side flange provided in a state bent from the inner peripheral edge of the second thrust trace portion to one side in the axial direction, and a part of the tip edge of the inner diameter side flange at a plurality of positions in the circumferential direction. A thrust roller bearing with a race, wherein the inner diameter side flange is provided so as to protrude radially outward from the leading edge of the inner diameter side flange, and the inner diameter side flange has an inner diameter of 30 to 80 mm. And the outer peripheral surface of the outer diameter side flange, the outer peripheral surface of the inner diameter side flange, and the inner and outer peripheral surfaces of the retainer, assuming that the both flanges and the cage are arranged concentrically. Between Cyclic sum of the radial dimension of the gap when the internal clearance of the thrust roller bearing with race, Lace thrust roller bearing, characterized in that the internal clearance is 1~2mm present, respectively.   The cage is formed by combining the first and second cage elements to form a hollow ring as a whole, and the first of these cage elements is arranged on the first thrust trace side. The cage element is formed by forming both first inner diameter side and first outer diameter side fitting cylindrical portions which are bent at right angles in the same direction with respect to the axial direction from both inner and outer peripheral edges of the annular first flat plate portion. And the second cage element disposed on the second thrust trace portion side is also in the same direction with respect to the axial direction from the inner and outer peripheral edges of the annular flat plate portion, and the first inner diameter side. The second inner diameter side and the second outer diameter side both fitting cylindrical part bent at a right angle in the opposite direction to the first outer diameter side both fitting cylindrical part, The inner cylindrical portion is fitted into the second inner diameter side fitting cylindrical portion, and the first outer diameter side fitting is performed. The both cage elements are combined with each other by fitting the cylindrical portion to the second outer diameter side fitting cylindrical portion, and the diameter of the second outer diameter side fitting cylindrical portion is set to the second flat plate portion. The first half on the side farther from the second flat plate part is larger than the proximal half on the side, and the first outer diameter side fitting cylindrical part is connected to the second outer diameter side fitting cylindrical part. The thrust roller bearing with a race according to claim 1, which is externally fitted only at the portion.   The second thrust trace is an annular second thrust trace portion, and at least one projecting piece provided in a state of projecting radially outward from a part of the outer peripheral edge of the second thrust trace portion; The outer diameter of the second thrust trace portion is smaller than the inner diameter of the outer diameter side flange, and the diameter of the circumscribed circle of the second thrust trace including the projecting piece is the outer diameter side flange. The thrust roller bearing with a race according to any one of claims 1 and 2, wherein the thrust roller bearing is larger than an outer diameter of the thrust roller bearing.   A thickness dimension of the projecting piece is smaller than a thickness dimension of the second thrust trace portion, and one side of the projecting piece facing the tip edge of the outer diameter side flange, and the second thrust trace portion. The thrust roller bearing with a race according to claim 3, wherein a step portion exists at a boundary portion between the roller and the race surface where the rollers are brought into rolling contact.   The thrust roller bearing with a race according to claim 4, wherein the protrusions are provided at a plurality of locations on the outer peripheral edge of the second thrust trace portion at equal intervals in the circumferential direction.

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