JP5821548B2 - Spacer for radial needle bearing - Google Patents

Description

  The present invention relates to an improvement of a spacer incorporated in a radial needle bearing for rotatably supporting, for example, a planetary gear constituting a planetary gear mechanism constituting an automatic transmission for an automobile around a planetary shaft supported by a carrier. Specifically, it can be configured at a low weight and at a low cost, and the rotational resistance (dynamic torque) of the radial needle bearing can be reduced by reducing the sliding resistance of the rubbing portion between the spacer and a mating member adjacent to the spacer. ), And a structure capable of reducing power loss of various rotary machine devices such as the automobile transmission incorporating the radial needle bearing.

[Description of prior art]
For example, a radial needle bearing in which a plurality of needles are arranged between an outer ring raceway and an inner ring raceway each having a cylindrical surface is widely used in a rotation support portion of a mechanical device such as an automatic transmission for automobiles. Further, the rotation support is operated in a state where a moment in a direction in which the central axes of both the members are inclined is applied between the outer diameter side member provided with the outer ring raceway and the inner diameter side member provided with the inner ring raceway. The part uses a double-row radial needle bearing in which a plurality of needles are arranged at two positions spaced apart in the axial direction to increase the rigidity against the moment. In order to ensure this moment rigidity, it is necessary to maintain the interval between the needles arranged in a double row, but in the case of a radial needle bearing, the axial position of each needle cannot be regulated as it is. Therefore, for example, a cylindrical spacer as described in Patent Documents 1 to 6 is arranged between the needles arranged in a double row so as to keep the distance between the needles. Yes.

  FIG. 4 is a plan view of a planetary gear constituting an automatic transmission for an automobile as an example of a rotation support device incorporating a double-row radial needle bearing provided with a spacer, which is conventionally known as described in each of the above patent documents. 1 shows a rotation support device 1 for a gear. The rotation support device 1 is configured such that a planetary gear 4 as an outer diameter side member is supported by a double row radial needle bearing unit 5 around an intermediate portion of a planetary shaft 3 as an inner diameter side member supported at both ends by a carrier 2. It is supported rotatably. The planetary gear 4 is a helical gear and meshes with a sun gear and a ring gear (both not shown) in a state in which the automobile automatic transmission is assembled. Therefore, an axial load is applied to the planetary gear 4 in addition to a radial load during operation of the automatic transmission for automobiles. As a result, the moment as described above is applied to the planetary gear 4.

  The double-row radial needle bearing unit 5 includes a pair of radial needle bearings 6 and 6 and a spacer 7 so as to have a structure capable of sufficiently securing rigidity against the moment as described above. In the example shown in the drawing, these radial needle bearings 6 and 6 are each formed by holding a plurality of needles 8 and 8 by means of substantially cylindrical cages 9 and 9 so as to be freely rollable. The rolling surfaces of these needles 8, 8 are a cylindrical inner ring raceway 10 provided on the outer peripheral surface of the planetary shaft 3, and a cylindrical outer ring raceway 11 provided on the inner peripheral surface of the planetary gear 4. In addition, they are in rolling contact with each other. The spacer 7 is disposed between the cages 9 and 9 of the radial needle bearings 6 and 6 to prevent the cages 9 and 9 from approaching each other. A so-called all-needle type double-row radial needle bearing unit in which a cage is omitted is also known. In the case of such a total needle type structure, one end surface in the axial direction of each needle is directly opposed to both end surfaces in the axial direction of the spacer. In any case, the spacer 7 secures the rigidity with respect to the moment by securing the inter-axial distance between the radial needle bearings 6, 6 arranged in a double row. Further, during the operation of the double row radial needle bearing unit 5, lubricating oil is supplied to both the radial needle bearings 6 and 6 through an oil supply passage 15 provided in the planetary shaft 3.

  For example, a spacer having a structure as shown in FIG. 5 has been known as the spacer 7 having the above-mentioned function. The spacer 7 includes a pair of rim portions 12 and 12 and a plurality of column portions 13 and 13. These rim parts 12, 12 are each annular and are arranged concentrically with respect to the axial direction. The column parts 13 and 13 are provided at a plurality of positions in the circumferential direction between the rim parts 12 and 12 so as to connect the rim parts 12 and 12 to each other. And the through-hole part 14 which makes both the inner and outer peripheral surfaces of the said spacer 7 connect the part surrounded by each of these four rim | limb parts 12 and 12 and said pillar parts 13 and 13 adjacent to the circumferential direction in each circumference | surroundings. , 14. Each of the through-hole portions 14 and 14 reduces the weight of the spacer 7 to reduce the inertial mass, and reduces the centrifugal force acting on the spacer 7 along with the revolving motion of the planetary shaft 3. It plays a function to suppress the bending. Further, the through holes 14 and 14 improve the performance of the rotary support device 1 based on stabilization of the supply of lubricating oil to the rolling contact portions of the both needle bearings 6 and 6 by securing a lubricating oil flow path. Furthermore, it also plays a role of cost reduction due to the material saving of the spacer 7. In the present specification and claims, the axial direction, radial direction, and circumferential direction refer to the axial direction, radial direction, and circumferential direction of the spacer unless otherwise specified.

  The spacer 7 as described above is assembled to the rotary support device 1, the outer peripheral surface is the outer ring raceway 11, and both axial end surfaces are the axial directions of the cages 9, 9 or the needles 8, 8. The end faces are brought into contact with or in close proximity to each other. In this state, lubricating oil is present in each of the contact portions or the proximity facing portions. During the operation of the rotation support device 1, the outer peripheral surface of the spacer 7 and the outer ring raceway 11 are connected to both axial end surfaces of the spacer 7 and the shafts of the cages 9 and 9 or the needles 8 and 8. The direction end faces are displaced relative to each other (rubbed). Since an oil film of lubricating oil exists in each of these rubbing portions, when the spacer 7 rotates relative to the adjacent member, the shear resistance acting on the oil film is large in the rotation resistance of the spacer 7. Occupy part. Such shear resistance increases as the facing area between the spacer 7 and the adjacent member increases.

  The frictional resistance based on the relative displacement between the spacer 7 and the member adjacent to the spacer 7 due to the shear resistance or the like as described above causes an increase in dynamic torque (torque loss generation) of the rotary support device 1. It becomes a cause of deteriorating the performance of various rotary machine devices such as an automatic transmission for automobiles incorporating the rotation support device 1. That is, there are various factors that increase the dynamic torque of the rotary support device 1, such as the rolling resistance and frictional resistance of the radial needle bearings 6 and 6 and the stirring resistance of the lubricating oil. The frictional resistance including the shearing resistance generated between the spacer 7 and the mating member and the agitation resistance of the lubricating oil accompanying the rotation of the spacer 7 are so large that they cannot be ignored. Therefore, in order to improve the performance of the rotary machine device incorporating the rotary support device 1, it is desirable to keep the resistance related to the spacer 7 low.

[Description of Prior Invention]
In view of the circumstances as described above, the area of the part where the spacer and the mating member abut or approach each other (hereinafter referred to as “opposing area”) is narrowed, and the rotational resistance (friction resistance including shear resistance) of this spacer is reduced. As an invention to be reduced, there is an invention according to Japanese Patent Application No. 2010-264249. This prior invention reduces the frictional resistance between the spacer and the mating member, reduces the torque loss during the operation of the rotary support device incorporating the double row radial needle bearing unit, and is also lightweight and can be manufactured at low cost. It is intended to realize a spacer structure.

  A radial needle bearing spacer that is a subject of the above-described invention (and the present invention described later) includes a cylindrical inner ring orbit provided on an outer peripheral surface of an inner ring equivalent member (same as an inner diameter side member) such as a planetary shaft, and a planet. Between a pair of radial needle bearings provided in an axially separated state between a cylindrical outer ring raceway provided on an inner peripheral surface of an outer ring equivalent member (same as an outer diameter side member) such as a gear. It is installed in the middle part. Each of the rim portions is annular and is provided in a state where the rim portions are connected to each other at a plurality of circumferential positions between the rim portions and a pair of rim portions arranged concentrically with respect to the axial direction. A plurality of pillars. Further, a portion surrounded by each of the four circumferences by both the rim portions and the column portions adjacent to each other in the circumferential direction is a through-hole portion that allows the inner and outer peripheral surfaces to communicate with each other. Then, the inner ring raceway, the outer ring raceway, and the radial needle bearings are incorporated into a space surrounded by the outer ring raceway, and the surface rotates relative to the counterpart member in a state where the surface is in contact with or in close proximity to the surface of the counterpart member. Do

  In particular, the radial needle bearing spacer according to the present invention is in contact with or in close proximity to the surface of the mating member in the state of being incorporated in the space at at least one of the rim portions and the pillar portions. A part of the part is recessed in a direction away from the mating member. Then, the frictional area between the mating member and the outer surface of the spacer is reduced by the area of the recessed portion, and the torque loss (dynamic torque, frictional resistance) of the double row radial needle bearing unit based on the presence of the spacer is reduced. ). The recessed portion includes a through-hole structure provided in a state of penetrating the inner and outer peripheral surfaces of the spacer as well as the bottomed recess.

As an aspect of the prior invention as described above, for example, the respective pillar portions are arranged intermittently in parallel with each other in the circumferential direction or in an inclined manner.
Alternatively, among the circumferential side surfaces of each column part, a recess is formed in a part or the whole in the axial direction, and the width dimension of each column part in the circumferential direction is defined in the part where these recesses are formed. It is made smaller than the width dimension of the through hole in the same direction.
Alternatively, the concave portions are formed in the axially outer side surfaces or outer peripheral edge portions of the both rim portions in a state where the concave portions are intermittently or continuously recessed with respect to the respective circumferential directions.
Alternatively, a recess is formed in each of the column portions, and the entire outer peripheral surface (outer diameter side surface) of each of the column portions is recessed inward in the radial direction from the outer peripheral surfaces of the two rim portions.
Or the axial direction intermediate part of each pillar part adjacent to the circumferential direction is mutually connected by the connection part provided in the state which spanned between these each pillar parts in the circumferential direction.

  According to the above-described prior invention, the frictional area between the surface of the radial needle bearing spacer and the outer ring raceway or the axial end surface of the cage or the axial end surface of each needle, which is the surface of the counterpart member, is reduced. Can be narrowed. And the double-row radial needle provided with the radial needle bearing spacer while suppressing the resistance (friction resistance including the shear resistance of the oil film) acting in the direction of suppressing the relative rotation between the radial needle bearing spacer and the mating member. The dynamic torque (torque loss) of the bearing unit can be reduced. In addition, the volume of the radial needle bearing spacer can be reduced by reducing the volume of the radial needle bearing spacer by providing the concave portion in order to reduce the frictional area with the surface of the mating member, thereby reducing the weight and cost of the radial needle bearing spacer. .

  Next, specific examples of the radial needle bearing spacer according to the present invention will be described with reference to FIGS. Each of the spacers 7a to 7k according to the prior invention described below and the spacers 7m to 7p according to the present invention to be described later is a pair arranged separately in the axial direction as shown in FIG. The radial needle bearings 6 and 6 are disposed between each other. Further, the outer peripheral surface is used in a state of sliding contact with or close to the outer ring raceway 11, and both axial end surfaces are in sliding contact with or close to the axial end surfaces of the cages 9, 9 or the needles 8, 8. . Each of the spacers 7a to 7p is an improvement made on the basis of the conventionally known spacer 7 shown in FIG. 5 described above. The description will be mainly omitted and the description common to the conventional structure will be omitted or simplified.

Further, the specifications (dimensions, material, surface roughness) of the spacers 7a to 7p of the present invention and the present invention are not particularly limited, but for example, the following specifications can be adopted.
Dimensions Inner diameter: 5-30mm
Radial thickness: 0.3-3.0mm
Axial width: 2-30mm
Circumferential width of the through-hole portion: 1 mm or more Axial width of the radially outer surface of the rim portion: 1 mm or more Material Iron-based alloy As the iron-based alloy, cold rolled steel plate (SPCC), ultra-low carbon steel (AISI-1010) ), Chrome molybdenum steel (SCM415) or the like, or those subjected to heat treatment such as carburizing or carbonitriding can be used. If these iron-based alloys are used, sufficient strength and rigidity can be ensured even in high-temperature environments. Synthetic resins Synthetic resins include polyacetal resin, polyamide resin (nylon 46, nylon 66), polyphenylene sulfide resin (PPS), etc. It can be used. If these synthetic resins are used, the spacer can be easily formed by injection molding, and not only the cost can be reduced, but also the above-described effects can be obtained by reducing the weight.
Surface Roughness Of the surface of the spacer, it is preferable that the outer peripheral surface and the axial end surface that are in contact with or in close proximity to the mating member are smooth surfaces in order to keep the frictional resistance during relative rotation with the mating member low. . Therefore, it is preferable that at least the outer peripheral surface and the axial end surface have a center line average roughness Ra of 6.3 μm or less.

"First example of the embodiment of the prior invention"
FIG. 6 shows the spacer 7a of the first example of the embodiment of the prior invention. The spacer 7a is configured such that the circumferential width of the axial intermediate portion of the plurality of column portions 13a, 13a arranged in parallel with each other is narrower than the circumferential width of both axial end portions, and each of the column portions 13a. , 13a is narrower than the circumferential width of each of the through holes 14a, 14a. In other words, one concave portion is provided in each circumferential side surface of each of the pillar portions 13a and 13a and is recessed in the circumferential direction at the axially intermediate portion of the circumferential side surfaces of the pillar portions 13a and 13a. 16 and 16 and the circumferential width w of the intermediate portion in the axial direction of each of the pillar portions 13a and 13a is made smaller than the circumferential width S of the intermediate portion in the axial direction of each of the through holes 14a and 14a ( w <S). Then, the area facing the inner ring raceway 10 (see FIG. 4) is narrowed on the outer peripheral surface of the spacer 7a by the radial opening area of each of the recesses 16 and 16. The circumferential width w of the intermediate portion in the axial direction of each of the column portions 13a and 13a is sufficiently smaller than the circumferential width W of the column portions 13 and 13 in the conventional structure shown in FIG. On the other hand, the circumferential widths at both axial ends of the pillars 13a and 13a are substantially the same as the circumferential width W related to the conventional structure. However, since the axial length of both ends in the axial direction where the circumferential width is wide is short, the circumferential width of the both ends in the axial direction may be slightly wider than the circumferential width W related to the conventional structure. .

  In addition, the shape and size (axial length, circumferential depth) of each of the recesses 16 and 16 can make the opposing area in consideration of the strength required for the column parts 13a and 13a. In order to make it as narrow as possible, we will regulate appropriately within the scope of the above-mentioned specifications. For example, the shape of each of the recesses 16 and 16 is trapezoidal in the structure shown in FIG. 6, but is not limited to the trapezoidal shape. For example, each of the column portions 13a and 13a such as an arc shape, an elliptical shape, a rectangular shape or the like. Any shape can be adopted as long as the strength and rigidity can be secured. Moreover, in the structure shown in FIG. 6, although the recessed parts 16 and 16 are each formed in the circumferential direction both sides of each pillar part 13a and 13a, you may form the recessed parts 16 and 16 only in any one side. In any case, the spacer 7a itself is only required to prevent the pair of radial needle bearings 6 and 6 arranged apart from each other in the axial direction from approaching each other. In particular, no large radial load or axial load is applied. Therefore, the required strength and rigidity are not particularly high. Therefore, even if each of the recesses 16 and 16 is enlarged to some extent for reducing the area of the outer peripheral surface of the spacer 7a or reducing the weight of the spacer 7a, a double row radial needle bearing unit incorporating the spacer 7a is used. There is no problem in terms of reliability and durability of 5 (see FIG. 4).

  According to the spacer 7a shown in FIG. 6, the circumferential width S of each of the through hole portions 14a and 14a is reduced by the amount corresponding to the reduction in the circumferential width w of the axial intermediate portion of each of the column portions 13a and 13a. The circumferential width s of each of the through holes 14 and 14 provided in the spacer 7 having the conventional structure shown in FIG. 5 is made larger (S> s). Then, the area of the outer peripheral surface of the spacer 7a including the outer diameter side surface of each column portion 13a, 13a is increased by the amount of the circumferential width S of the respective through-hole portions 14a, 14a being increased. 7 is narrower than the area of the outer peripheral surface. Then, by reducing the area of the outer peripheral surface, it acts between the outer peripheral surface of the spacer 7a and the outer ring raceway 11 (see FIG. 4) formed on the inner peripheral surface of the outer diameter side member such as the planetary gear 4. The frictional resistance including the aforementioned shearing resistance can be reduced. As a result, the dynamic torque of the double row radial needle bearing unit 5 (see FIG. 4) incorporating the spacer 7a can be kept small, and the performance of the rotary machine device of the double row radial needle bearing unit 5 can be improved. In addition, the spacer 7a is reduced in weight and reduced in cost by reducing the raw material by forming the recesses 16 and 16 in the respective pillars 13a and 13a to reduce the circumferential width w of the axial intermediate portion. I can plan. In addition, weight reduction contributes to suppression of the bending of inner diameter side members, such as the planetary shaft 3 (refer FIG. 4) based on the centrifugal force which generate | occur | produces (with revolving motion) at the time of a driving | operation.

"Second example of the embodiment of the prior invention"
FIG. 7 shows the spacer 7b of the second example of the embodiment of the prior invention. In the case of this example, conversely to the case of the first example described above, recesses 16a and 16a are formed on both side surfaces in the circumferential direction of both end portions in the axial direction of the respective column portions 13b and 13b, respectively. The outer diameter side surfaces of the portions 13b and 13b, that is, the area of the outer peripheral surface of the spacer 7b are made narrower than the conventional structure shown in FIG. That is, in the case of this example, the circumferential width of the intermediate portion in the axial direction of each of the pillar portions 13a, 13a is set to the same level as in the conventional structure, and the circumferential width at both axial end portions is narrower than this. doing.
Since other configurations and operations / effects are the same as those in the first example described above, redundant description is omitted.

"Third example of the embodiment of the prior invention"
FIG. 8 shows a spacer 7c of the third example of the embodiment of the prior invention. The spacer 7c has a structure that combines the first example described above and the second example described above. That is, in the case of the structure of this example, the recesses 16b, 16b are formed on both sides in the circumferential direction of the intermediate portion in the axial direction of the pillars 13c, 13c, and the recesses 16a, 16a are formed on both sides in the circumferential direction at both ends in the axial direction. Each is formed. The area of the outer side surface of each of the column portions 13c and 13c, and hence the area of the outer peripheral surface of the spacer 7c, is reduced by the amount of the recesses 16b and 16a.
Since other configurations and operations / effects are the same as those in the first example and the second example described above, a duplicate description is omitted.

"Fourth example of the embodiment of the prior invention"
FIG. 9 shows a spacer 7d of the fourth example of the embodiment of the prior invention. The spacer 7d has recesses 16b and 16b formed at two positions on both side surfaces in the circumferential direction of the intermediate portion in the axial direction of the pillars 13d and 13d, respectively. The area of the outer side surface of each of the pillar portions 13d and 13d, that is, the area of the outer peripheral surface of the spacer 7d is reduced by the amount of each of the recesses 16b and 16b.
Since other configurations and operations / effects are the same as those in the above-described first and second examples and the above-described third example, overlapping description will be omitted.

"Fifth example of embodiment of prior invention"
FIG. 10 shows a spacer 7e of the fifth example of the embodiment of the prior invention. The spacer 7e has a partially conical convex inclined surface portion 17 on the radially outer side portion of the pair of rim portions 12a, 12a each having an annular shape, on the radially outer side surface (the axial side surface opposite to each other). , 17 are formed, and the radially outward portion is recessed in a direction away from the mating member. On the other hand, the radially inward portions of the outer side surfaces in the axial direction of the rim portions 12a and 12a are flat surfaces 18 and 18 that exist in a direction perpendicular to the central axis of the spacer 7e. In addition, the size (axial dimension and radial dimension) of both the inclined surface portions 17 and 17 is, for example, as large as possible within a range in which the strength and rigidity of the both rim portions 12a and 12a can be secured. This is also preferable from the viewpoint of reducing the rubbing area and reducing the weight of the spacer 7e. For example, the axial dimension is about 1/2 to 3/4 of the axial width of the rim parts 12a and 12a, and the radial dimension is 1 of the radial thickness of the rim parts 12a and 12a. It is preferable to set it to about / 2 to 3/4. In addition, the inclination angle of the two inclined surface portions 17 and 17 with respect to the central axis of the spacer 7e is set in a range of more than 0 ° and less than 90 °, but is preferably set in a range of 30 to 60 °.

A cage in which the flat surfaces 18 and 18 constitute a pair of radial needle bearings 6 and 6 in a state in which the spacer 7e configured as described above is incorporated in the double row radial needle bearing unit 5 (see FIG. 4). 9, 9 or the axial end surfaces of the needles 8 and 8 (see FIG. 4) abut or face each other. The areas of the flat surfaces 18 and 18 are narrower than the areas of the end faces in the axial direction of the rim portions 12 and 12 of the conventional structure shown in FIG. 5 based on the presence of the inclined surface portions 17 and 17. Therefore, in the case of this example, it is possible to reduce the frictional resistance associated with the relative rotation between the spacer 7e and the retainers 9, 9 or the needles 8, 8. Further, the facing area between the outer peripheral surfaces of the rim portions 12a, 12a and the outer ring raceway 11 (see FIG. 4) is narrowed, and the spacer 7e, the planetary gear 4 (see FIG. 4), etc. Friction resistance accompanying relative rotation with the diameter side member can be reduced. And the dynamic torque of the double row radial needle bearing unit 5 can be reduced. Furthermore, the volume of the spacer 7e can be reduced and the weight can be reduced by forming the both inclined surface portions 17 and 17.
The structure of this example can also be implemented in combination with the structures of the first to fourth examples described above.
Since other configurations and operations / effects are the same as those in the first to fourth examples described above, redundant description will be omitted.

"Sixth example of embodiment of prior invention"
FIG. 11 shows a spacer 7f of a sixth example of the embodiment of the prior invention. The spacer 7f has a pair of rim portions 12b, 12b each having an annular shape, and the outer surfaces in the axial direction of the pair of rim portions 12b, 12b are intermittently recessed in the axial direction with respect to the circumferential direction. Yes. In the illustrated example, each of the recesses 19 is formed in a substantially rectangular shape penetrating from the inner periphery to the outer periphery of the axially outer side surfaces of the rim portions 12b, 12b. In the illustrated example, the recesses 19 are arranged at an equal pitch in the circumferential direction, but it is not always necessary to have an equal pitch.

  In any case, the size (circumferential width, axial depth) of the recesses 19, 19 is, for example, the size (diameter, radial thickness, axial width) of the rim portions 12b, 12b. Accordingly, it is possible to set as large as possible within a range in which the strength and rigidity required for the two rim portions 12b and 12b can be secured in a state after the respective recesses 19 and 19 are formed. This is preferable from the viewpoint of reducing torque loss by reducing the facing area of the spacer and reducing the weight of the spacer 7f. For example, the circumferential width of each of the recesses 19 and 19 is set to about 1 to 2 times the circumferential width of the projections existing between the recesses 19 and 19 adjacent to each other in the circumferential direction. The axial depth is preferably set to about 1/3 to 2/3 of the axial width of the rim portions 12b, 12b.

Further, the shape of each of the recesses 19 and 19 is not limited to the rectangular shape as illustrated, and various shapes such as a partial arc shape, an elliptical shape, and a triangular shape can be employed. In the example shown in the figure, the recesses 19 and 19 and the pillars 13 and 13 are made to coincide with each other with respect to the phase in the circumferential direction, but the phases of the recesses 19 and 19 and the pillars 13 and 13 are the same. May be shifted by a half pitch so that the phase of each of the recesses 19 and 19 and the phase of each of the through holes 14 and 14 coincide with each other. Further, the number of the concave portions 19 and 19 formed on the outer side surfaces in the axial direction of the rim portions 12b and 12b is different from the number of the column portions 13 and 13 (the through-hole portions 14 and 14). Also good.
The structure of this example can also be implemented in combination with the structures of the first to fifth examples described above.
Since other configurations and operations / effects are the same as those in the first to fifth examples described above, redundant description is omitted.

"Seventh example of the embodiment of the prior invention"
FIG. 12 shows a spacer 7g of the seventh example of the embodiment of the prior invention. The spacer 7g has a pair of rim portions 12c and 12c that are discontinuous in the circumferential direction. That is, the rim parts 12c, 12c are each a plurality of (six in the illustrated example) rim elements 20, 20 each having a partial arc shape, between the rim parts 12c, 12c. The phase in the circumferential direction is arranged by being shifted by a half pitch. As the spacer 7g, both end edges in the circumferential direction of the rim elements 20 and 20 are made continuous by the column parts 13 and 13, respectively, and the whole is cylindrical, and the shape in the unfolded state is crank-shaped. Yes. In the structure of this example, the discontinuous portions between the rim elements 20 and 20 that are adjacent to each other in the circumferential direction are portions that are recessed in a direction away from the counterpart member.

The discontinuous portion is preferably formed at the same time as the spacer 7g is integrally formed by injection molding of synthetic resin from the viewpoint of saving material and facilitating processing. However, when the spacer 7g is made of a metal material, a part of the rim portions 12 and 12 constituting the cage 7 having the conventional structure shown in FIG. it can. In any case, the outer peripheral surface and the axially outer surface of both the rim portions 12c and 12c, the outer ring raceway 11 and the cages 9 and 9 or the needles 8 in the spacer 7g are provided for the discontinuous portion. , 8 can be reduced in the area facing the axial end face (see FIG. 4).
The structure of this example can also be implemented in combination with the structures of the first to sixth examples described above.
Since other configurations and operations / effects are the same as those in the first to sixth examples described above, a duplicate description is omitted.

“Eighth Example of Embodiment of Prior Invention”
FIG. 13 shows the spacer 7h of the eighth example of the embodiment of the prior invention. This spacer 7h exists between the column portions 13 and 13 adjacent to each other in the circumferential direction by reducing the number of the column portions 13 and 13 and increasing the circumferential pitch with respect to the conventional structure shown in FIG. The opening areas of the through-hole portions 14b and 14b are widened, and the area of the outer peripheral surface facing the outer ring raceway 11 (see FIG. 4) is narrowed. In the structure of this example, at the circumferential end portions of the respective through-hole portions 14b, 14b, the portions that are wider than the through-hole portions 14, 14 of the conventional structure (see FIG. 5) are away from the mating member. It becomes the part dented in.

  The number of the pillar portions 13 and 13 constituting the spacer 7h is required to be three or more, but it is preferable that the number is smaller as long as the strength and rigidity of the spacer 7h can be secured. The circumferential width of each of the through holes 14b and 14b is preferably larger than the circumferential width of each of the pillars 13 and 13, but at least the circumferential width of each of the through holes 14b and 14b. Two or more times, preferably three times or more, the circumferential width of each of the pillars 13 and 13 is secured. The upper limit of the circumferential width of each of the through-hole portions 14b and 14b is defined as a value that can secure the required rigidity after setting the number of the column portions 13 and 13 to three or more. As long as this condition is satisfied, the circumferential width of each of the through holes 14b, 14b is preferably as large as possible.

The wide through holes 14b and 14b are preferably formed at the same time as the spacer 7h is integrally formed by injection molding of synthetic resin from the viewpoint of saving materials and facilitating processing. However, when the spacer 7h is made of a metal material, a part (one or two) of the column parts 13 and 13 constituting the cage 7 having the conventional structure shown in FIG. The column portions 13 and 13 can be formed by scraping (thinning) later.
The structure of this example can also be implemented in combination with the structures of the first to seventh examples described above.
Since other configurations and operations / effects are the same as those in the first to seventh examples described above, a duplicate description is omitted.

"Ninth example of embodiment of prior invention"
FIG. 14 shows a spacer 7i of the ninth example of the embodiment of the prior invention. The spacer 7i of this example is an improvement of the structure of the spacer 7h of the eighth example described above, and has a structure in which a reinforcing rim portion 21 is added to the intermediate portion in the axial direction. That is, the reinforcing rim portion 21 is provided in a state in which the axial intermediate portions of the column portions 13 and 13 are connected to each other so as to partition the wide through-hole portions 14b and 14b in the axial direction. The reinforcing rim portion 21 has the same diameter as the pair of rim portions 12 and 12 provided at both end portions in the axial direction, and is concentric with both the rim portions 12 and 12. In the case of this example, the reinforcing rim portion 21 is provided so that the strength and rigidity of the spacer 7i can be sufficiently ensured even if the circumferential widths of the through-hole portions 14b and 14b are sufficiently large. ing.
Other configurations, operations, and effects are the same as those in the eighth example described above, including the points that can be combined with other forms, and thus redundant description is omitted.

"Tenth example of the embodiment of the prior invention"
FIG. 15 shows the spacer 7j of the tenth example of the embodiment of the prior invention. In the case of the spacer 7j, an even number (six in the illustrated example) of column portions 13d and 13e disposed between the pair of rim portions 12 and 12 are inclined with respect to the axial direction. The inclination direction is opposite to each other between the column portions 13d and 13e adjacent to each other in the circumferential direction. In this way, by tilting each of the column portions 13d and 13e and making the structure of the spacer 7j into a truss shape, the twisting direction and the axial force acting between the rim portions 12 and 12 are described above. The strength and rigidity of the spacer 7j are improved compared to the eighth example described above.
In addition, when this example is combined with the structure of the ninth example described above, the strength and rigidity of the spacer 7j can be further improved.
Other configurations, operations, and effects are the same as those of the eighth example described above, including that they can be implemented in combination with the structures of the first to seventh examples described above, and thus redundant descriptions are omitted.

"Eleventh example of the embodiment of the prior invention"
16 to 17 show an eleventh example spacer 7k according to the embodiment of the present invention. In the case of the spacer 7k, the thickness in the radial direction of each of the column portions 13f and 13f is made smaller than the spacer 7 having the conventional structure shown in FIG. Further, the radially inner side surfaces of these pillar portions 13f and 13f and the inner peripheral surfaces of the pair of rim portions 12 and 12 are positioned on a single cylindrical surface. And the whole radial direction outer side surface of each pillar part 13f and 13f is dented in the radial direction inner side rather than the outer peripheral surface of both the said rim | limb parts 12 and 12. FIG. In the structure of this example, the radially outer surface of each of the pillar portions 13f and 13f is a portion that is recessed in a direction away from the counterpart member.
The extent to which the radial thickness of each of the column portions 13f, 13f is smaller than the radial thickness of the rim portions 12, 12 can be increased as much as possible to ensure the strength and rigidity of the spacer 7k. This is preferable in terms of reducing the weight of the spacer 7k. From the surface where the frictional resistance with the outer ring raceway 11 (see FIG. 4) which is the mating surface is kept low, the radially outer surface of each of the column portions 13f and 13f is slightly smaller than the outer peripheral surface of both the rim portions 12 and 12 ( If it is recessed (for example, 0.5 mm or more, preferably 1 mm or more), it is possible to prevent the oil film from being formed on the portion and sufficiently reduce the frictional resistance.
The structure of this example is lighter than the structures of the fifth to seventh examples described above from the aspect of reducing the frictional resistance with the axial end surfaces of the cages 9 and 9 or needles 8 and 8 (see FIG. 4). From the aspect of achieving the above, the structures of the fifth to tenth examples described above can be combined with each other.
Since other configurations and operations / effects are the same as those of the first to tenth examples described above, a duplicate description is omitted.

  The radial needle bearing spacer of the previous invention has the structure as described above, and can obtain an effect such as reducing torque loss during operation of the rotary support device. However, while ensuring strength and rigidity, this torque can be obtained. There is room for improvement in terms of further reducing the loss. That is, the radial needle bearing spacer which is the subject of the previous invention and the present invention has a high possibility that the outer peripheral surface and the outer ring raceway rotate relative to each other during operation of the rotary support device. For this reason, it is necessary to make an appropriate oil film exist in the rubbing portion in order to prevent the occurrence of significant wear due to the oil film breakage in the rubbing portion between the outer peripheral surface and the outer ring raceway. On the other hand, as described above, when the area of the oil film is increased, a large shear resistance is generated in the oil film portion at the time of relative rotation between the outer peripheral surface and the outer ring raceway, and the double row radial needle constituting the rotation support device. The dynamic torque (torque loss) of the bearing increases.

JP 2005-16710 A JP 2005-325992 A JP 2008-101725 A JP 2008-303992 A JP 2009-115323 A JP 2010-2029 A

  In view of the circumstances as described above, the present invention has a double-row radial needle while suppressing an abrasion of each part by making an appropriate (non-excessive area) oil film in a frictional part between the outer peripheral surface and the outer ring raceway. This invention was invented to realize a radial needle bearing spacer that can keep the dynamic torque of the bearing low.

The radial needle bearing spacer of the present invention has an axial direction between a cylindrical inner ring raceway provided on the outer peripheral surface of the inner ring equivalent member and a cylindrical outer ring raceway provided on the inner peripheral surface of the outer ring equivalent member. It is installed in the part between a pair of radial needle bearings provided in a state separated from each other.
Such radial needle bearing spacers are each annular, a pair of rim portions arranged concentrically with each other in an axially separated state, and a plurality of circumferential directions between these rim portions, And a plurality of column portions provided in a state of connecting both the rim portions.

In particular, in the radial needle bearing spacer of the present invention, at least the surface of each column portion has a bottomed bottom that is recessed inward in the radial direction on the outer diameter side that is the outer side in the radial direction. A radial recess is provided. And the part which surrounds each of these radial direction recessed parts in each perimeter is located outside in the radial direction rather than each of these radial direction recessed parts.
When implementing such a radial needle bearing spacer according to the present invention, for example, as in the invention described in claim 2, the radial recesses are formed on the outer diameter side surfaces of the column portions in the axial direction. . Then, both ends in the circumferential direction of the respective radial recesses are partitioned by both ends in the circumferential direction of the respective column portions, and both ends in the axial direction are similarly partitioned by the both rim portions.
Alternatively, as in the invention described in claim 3, each of the radial recesses is a circular recess formed on the outer diameter side surface of each of the column portions at a plurality of positions for each of the column portions.

Further, when the radial needle bearing spacer of the present invention as described above is implemented, it is preferable that, as in the invention described in claim 4, the axially opposite side surfaces of the two rim portions are opposite to each other. An axial recess that is recessed inward in the axial direction is formed on the axially outer side surface that is a side surface.
When carrying out the invention described in claim 4, for example, as in the invention described in claim 5, the axial concave portion is placed around the entire circumference in the radial intermediate portion of the outer surfaces of the rim portions. An annular recess formed over the area.
Or like the invention described in Claim 6, the said axial direction recessed part is made into the circular recessed part formed in the outer surface of the said both rim | limb part by several places for each of these rim | limb parts.

According to the radial needle bearing spacer of the present invention configured as described above, an appropriate oil film is present in the frictional portion between the outer peripheral surface and the inner ring raceway, and the wear of each part is suppressed, while the double row radial needle bearing is Dynamic torque can be kept low.
That is, during operation of the double-row radial needle bearing incorporating the radial needle bearing spacer of the present invention, lubrication is provided in each radial recess formed on the outer diameter side surface of each column portion constituting the radial needle bearing spacer. Oil is stored. Then, the lubricating oil enters between the outer peripheral surface of the radial needle bearing spacer and the outer ring raceway with the relative rotation of the radial needle bearing spacer and the outer ring equivalent member, and forms an oil film in the portion. . For this reason, it is possible to prevent the occurrence of significant wear due to oil film breakage at the rubbing portion between the outer peripheral surface and the outer ring raceway. On the other hand, since the distance between the bottom surface of each of the radial recesses and the outer ring raceway can be sufficiently ensured, the lubricating oil stored in each of the radial recesses generates a large shear resistance even during the relative rotation. There is nothing. As a result, as described above, the dynamic torque can be kept low while suppressing the wear of each part.
Furthermore, according to the invention described in claim 4, the lubrication state between the axial end surface of the radial needle bearing spacer and the axial end surface of the cage or each needle constituting the radial needle bearing can be improved.

The perspective view of the spacer for radial needle bearings which shows the 1st example of embodiment of this invention. The perspective view which shows the 2nd example. The perspective view which shows the 3rd example. Sectional drawing which shows an example of the rotation support apparatus by the double row radial needle bearing unit incorporating the spacer used as the object of this invention. The perspective view which shows an example of the conventional structure of the spacer for radial needle bearings. The perspective view which shows the 1st example of the spacer for radial needle bearings concerning a prior invention. The perspective view which shows the 2nd example. The perspective view which shows the 3rd example. The perspective view which shows the 4th example. The perspective view which shows the 5th example. The perspective view which shows the 6th example. The perspective view which shows the 7th example. The perspective view which shows the 8th example. The perspective view which shows the 9th example. The perspective view which shows the 10th example. The perspective view which shows the 11th example. XX sectional drawing of FIG.

[First example of embodiment]
FIG. 1 shows a first example of an embodiment of the present invention corresponding to claims 1 and 2. The spacer 7m of this example is characterized by providing bottomed radial recesses 22 and 22 that are recessed inward in the radial direction on the outer diameter side surfaces of the pillars 13g and 13g, and the spacer 7m and the planetary gear. 4 (refer to FIG. 4) and the like to smoothly rotate relative to the outer diameter side member. Since the basic configuration of the spacer 7m excluding the radial recesses 22 and 22 is the same as that of the spacer 7 having the conventional structure shown in FIG. 5 described above, the overlapping description will be omitted or simplified. The description will focus on the features of the example. The specifications (dimensions, material, and surface roughness) that can be used as the spacer 7m are the same as those in the above-described prior invention.

  In the case of this example, the inner diameter side surface of each of the column portions 13g and 13g and the inner peripheral surface of the pair of rim portions 12 and 12 are arranged on a single cylindrical surface, and the circumference of the outer diameter side surface of each of the column portions 13g and 13g. Both end portions in the direction and the outer peripheral surfaces of the rim portions 12, 12 are respectively positioned on a single cylindrical surface. And each said radial direction recessed part 22 and 22 is each formed in the circumferential direction intermediate part of each said column part 13g, 13g. In the case of this example, each of these radial recesses 22 and 22 is formed over the entire length of each of the column portions 13g and 13g. The cross-sectional shapes (bottom surfaces of the bottom surfaces) of the radial recesses 22 and 22 with respect to a virtual plane orthogonal to the central axis of the spacer 7m are the same composite arc over the entire length. This composite arc has a concave portion on the radially outer side at the center in the width direction with respect to the circumferential direction, and is also convex at both ends in the width direction. Further, the ends of the respective arcs are smoothly continuous with each other, and both the circumferential edges of the radial recesses 22 and 22 and the outer circumferential surfaces of the circumferential ends of the pillars 13g and 13g are smoothly continuous. doing. With the above configuration, both circumferential ends of the radial recesses 22 and 22 are partitioned by the circumferential ends of the column portions 13g and 13g, and both axial ends are similarly partitioned by the rim portions 12 and 12, respectively. ing.

  When the spacer 7m of the present example configured as described above is incorporated in the rotation support device 1 as shown in FIG. 4 described above, the outer diameter side surfaces of the pillar portions 13g and 13g and the outer ring raceway 11 face each other. . In each of the radial recesses 22, 22, lubricating oil that is fed from the oil supply passage 15 to the inner diameter side of the outer ring raceway 11 is stored. In this state, when the spacer 7m and the outer ring raceway 11 are relatively displaced in the rotational direction, the lubricating oil stored in the radial recesses 22 and 22 is caused between the outer peripheral surface of the spacer 7m and the outer ring raceway 11. The oil film is formed in the part. For this reason, it is possible to prevent the occurrence of significant wear due to the oil film breakage at the rubbing portion between the outer peripheral surface and the outer ring raceway 11. On the other hand, since the distance between the bottom surface of each of the radial recesses 22 and 22 and the outer ring raceway 11 can be sufficiently secured in the radial direction, the lubricating oil stored in each of these radial recesses 22 and 22 is Even during relative rotation, a large shear resistance does not occur. As a result, as described above, the dynamic torque can be kept low while suppressing the wear of each part.

In order to keep the shear resistance low, it is necessary to ensure a sufficient radial depth (at least 0.5 mm or more, preferably 1 mm or more) of the radial recesses 22 and 22. As the radial depth is increased, the radial thickness of the central portion in the circumferential direction of each of the column portions 13g and 13g is reduced, but the radial thickness at both ends in the circumferential direction is not reduced. Accordingly, the section modulus of each of the pillar portions 13g and 13g can be sufficiently secured, and the strength and rigidity of the spacer 7m including these pillar portions 13g and 13g can be sufficiently secured.
In addition, the structure of this example can also be implemented in combination with the 5th to 10th examples of the above-described embodiment of the present invention.
Since the configuration and operation of the other parts are the same as those of the previous invention described above, redundant description will be omitted.

[Second Example of Embodiment]
FIG. 2 shows a second example of an embodiment of the present invention corresponding to claims 1, 2, 4, and 5. In the case of the spacer 7n of this example, an annular recess 23 is formed over the entire circumference in the radial intermediate portion of the axially outer side surface of the pair of rim portions 12d, 12d provided at both axial end portions. Yes. When the spacer 7n of this example having such an annular recess 23 is incorporated in the rotary support device 1 as shown in FIG. 4 described above, the axially outer side surfaces of the rim portions 12d and 12d and the cage 9, 9 or the axial end surfaces of the needles 8 and 8 are close to each other. Further, in both the annular recesses 23, lubricating oil fed from the oil supply passage 15 to the inner diameter side of the outer ring raceway 11 is stored.

In this state, when the spacer 7n and the cages 9 and 9 or the needles 8 and 8 are relatively displaced in the circumferential direction, the lubricating oil stored in the annular recesses 23 is transferred to the spacer 7n and the both The cages 9 and 9 or the needles 8 and 8 enter between the axial end surfaces to form an oil film in the portions. For this reason, it is possible to prevent the occurrence of significant wear due to oil film breakage at the rubbing portion between the spacers 7n and the retainers 9, 9 or the needles 8, 8. On the other hand, since the distance between the bottom surfaces of the annular recesses 23 and the axial end surfaces of the cages 9 and 9 or the needles 8 and 8 can be sufficiently secured in the axial direction, the reservoirs are stored in the annular recesses 23. With respect to the lubricating oil, no great shear resistance is generated even during the relative rotation. As a result, as described above, the dynamic torque can be kept low while suppressing the wear of each part. If the rim portions 12d and 12d are sufficiently thick in the radial direction, a plurality of annular recesses can be formed concentrically on the outer surfaces of the rim portions 12d and 12d in the axial direction.
Since the configuration and operation of the other parts are the same as those in the first example of the above-described embodiment, including the possibility of combination with the structure of the previous invention, the same parts are denoted by the same reference numerals, and redundant description is given. Is omitted.

[Third example of embodiment]
FIG. 3 shows a third example of an embodiment of the present invention corresponding to claims 1, 3, 4, and 6. In the case of the spacer 7p of this example, a plurality of circular recesses 24, 24, each being a recess in the radial direction, are formed on the outer diameter side surfaces of the pillars 13, 13, respectively, for each of the pillars 13, 13. doing. In addition, circular recesses 25 and 25, each of which is an axial recess, are formed on the axially outer side surfaces of the pair of rim portions 12 and 12 formed at both axial ends of the spacer 7p. Are formed at multiple locations. Each of these circular recesses 24 and 25 is a partially spherical recess. Such circular recesses 24 and 25 also function in the same manner as the axial recesses 22 and 22 and the annular recess 23 in the second example of the embodiment described above, and suppress the wear of each part, while reducing the dynamic torque. It contributes to keeping low.
Since the configuration and operation of the other parts are the same as those of the second example of the above-described embodiment, including the possibility of combination with the structure of the previous invention, overlapping description will be omitted.

  The spacer for radial needle bearings of the present invention can be used for a radial needle bearing constituting a rotation support part of various mechanical devices. When applied to the rotation support portion of the planetary gear constituting the planetary gear device, the invention is not limited to the automatic transmission for automobiles, and can be applied to the rotation support portion of a rotation member other than the planetary gear.

  In addition, the structure of the present invention and the structure according to the previous invention can be combined as appropriate. For example, as in the third example of the embodiment of the present invention shown in FIG. 3, the structure in which the circular concave portion is provided can be implemented in combination with any of the first to eleventh examples of the above-described embodiment of the present invention. The structure shown in FIGS. 1 and 2 in which the radial recesses are formed in the axial direction on the outer diameter side surfaces of the pillars is shown in FIGS. It can be implemented in combination with the fifth to eleventh examples shown. Also, the first to fourth examples shown in FIGS. 6 to 9 can be combined and implemented if the radial recesses are formed in a portion having a large circumferential width in the column portion. Further, the structure shown in FIG. 2 in which the annular recesses are formed on the outer side surfaces of both rims is not the fifth to seventh examples shown in FIGS. Can be implemented in combination.

DESCRIPTION OF SYMBOLS 1 Rotation support apparatus 2 Carrier 3 Planetary shaft 4 Planetary gear 5 Double row radial needle bearing unit 6 Radial needle bearing 7, 7a-7p Spacer 8 Needle 9 Cage 10 Inner ring track 11 Outer ring track 12, 12a Rim part 13, 13a-13g Pillar part 14, 14a, 14b Through-hole part 15 Oil supply passage 16, 16a Concave part 17 Inclined surface part 18 Flat surface 19 Concave part 20 Rim element 21 Reinforcing rim part 22 Radial concave part 23 Annular concave part 24 Circular concave part 25 Circular concave part

Claims (6)

A pair provided in an axially separated state between a cylindrical inner ring raceway provided on the outer peripheral surface of the inner ring equivalent member and a cylindrical outer ring raceway provided on the inner peripheral surface of the outer ring equivalent member. Of radial needle bearings,
In a state in which each rim portion is connected to a pair of rim portions arranged concentrically with each other in an annular shape and spaced apart in the axial direction, and a plurality of circumferential directions between these rim portions. In a radial needle bearing spacer provided with a plurality of provided pillars,
At least the surface of each column portion is provided with a bottomed radial concave portion that is recessed inward in the radial direction on the outer radial side surface that is the outer side surface in the radial direction, A radial needle bearing spacer characterized in that a portion surrounded by a circumference is positioned outward in the radial direction with respect to each of the radial recesses.   The respective radial recesses are formed in the axial direction on the outer diameter side surfaces of the respective column parts, and both circumferential ends of the respective radial recesses are also axially formed by the circumferential end edges of the respective column parts. The radial needle bearing spacer according to claim 1, wherein both end portions are respectively partitioned by the both rim portions.   The radial needle bearing spacer according to claim 1, wherein each of the radial recesses is a circular recess formed on the outer diameter side surface of each of the column portions at a plurality of locations for each of the column portions.   The axial direction recessed part recessed inward with respect to the axial direction is formed in the axial direction outer side surface which is a mutually opposite side surface among the axial direction both sides | surfaces of both the said rim | limb parts, The Claims 1-3 The radial needle bearing spacer described in any one of the above.   The radial needle bearing spacer according to claim 4, wherein the axial recess is an annular recess formed over the entire circumference in a radially intermediate portion of the outer surfaces of the two rim portions.   The radial needle bearing spacer according to claim 4, wherein the axial recess is a circular recess formed on the outer surface of each of the rim portions at a plurality of locations for each of the rim portions.

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