JP2007100791A - Tapered roller bearing and bearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To compensate differences of thermal expansion and contraction between a shaft and a case body by using a compensation ring member to prevent a preload escape phenomenon of a tapered roller bearing caused by temperature rise. <P>SOLUTION: An outer ring 13 having an outer peripheral face fitted into a stepped hole 12 of a housing 11 and an inner ring 15 fitted into the shaft 14 are provided. Between an outer ring raceway surface 16 of the outer ring 13 and an inner ring raceway surface 17 of the inner ring 15, a plurality of tapered rollers 18 are rotatably supported by a cage 19. An inner ring large end face 15a of the inner ring 15 is made contact with a shoulder part 14a of the shaft 14 and held by the shaft 14. An outer ring large end face 13a of the outer ring 13 is held by a shoulder part 12a of the stepped hole 12 of the housing 11 via a compensation ring 21. The compensation ring 21 is constituted by a belleville spring or wave spring, has a function to compensate the differences of thermal expansion and contraction between the housing 11 and the shaft 14, and is made contact with and held by a recessed part 23 defined by the outer ring large end face 13b of the outer ring 13 and the shoulder part 12a of the stepped hole 12. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a rolling bearing used in an automobile, a motor, a machine tool, and the like, and more particularly, to a tapered roller bearing and a bearing device provided so as to compensate for a difference in thermal expansion and contraction between a housing and a shaft.

  In an effort to reduce the weight of the machine, the machine manufacturer switched the housing to a lightweight aluminum alloy or a lightweight magnesium alloy. However, the shaft attached to the gear that rotates in these cases and transmits torque remains steel. The reason is that steel has high strength and rigidity and is excellent in wear resistance. When a tapered roller bearing is used to attach the shaft to the housing, the shaft is supported by two single row tapered roller bearings attached in series to each other. A gear is engaged with the shaft, and a radial load and a thrust load are applied to the bearing by the meshing reaction force of the gear.

  Tapered roller bearings hold very large loads relative to their dimensions. In addition, they can support radial and thrust loads simultaneously. These properties help make the machine very compact. In order to obtain large shaft rigidity and bearing rigidity with respect to these loads, a preload is generally applied to the bearing in many cases. Preload may be applied to the bearing outer ring large end face or inner ring large end face with a fixed position preload applied, or the bearing outer ring large end face or inner ring large end face may be loaded with a fixed position preload by screws. Considering the convenience of assembly, the bearings may be configured as a front combination. In the case of a combination of a casing having a large thermal expansion coefficient and a shaft having a small thermal expansion coefficient compared to it, the preload set at the initial stage decreases as the temperature rises when the front combination is used, and preload loss occurs when the temperature rises further. Further, when the temperature falls, the preload set in the initial stage becomes large, and when the temperature falls further, the preload becomes excessive, which can cause seizure and a short life (see, for example, Patent Document 1).

JP-A-5-99223

  Ideally, the two combined tapered roller bearings should operate within the optimum set range indicated in the application requirements. In general, the objective is to minimize axial and radial free movement of the shaft, maximize bearing life, reduce noise and improve gear engagement. When the preload loss occurs, the shaft rigidity and the bearing rigidity are reduced, and abnormal noise due to a change in the meshing point of the gear, reduction in gear strength, reduction in bearing life due to bearing play, and abnormal noise due to the bearing are generated. In addition, in an automobile transmission, there may be an increase in operating force when changing gears.

  In view of the above-described problems, the present invention uses a compensation phosphorus member to prevent the occurrence of a preload loss phenomenon of a combined tapered roller bearing due to a temperature rise. It is an object of the present invention to provide a tapered roller bearing and a bearing device that compensate for the above.

In order to solve the above-mentioned problem, an invention according to claim 1 includes an outer ring having a conical track surface on an inner peripheral surface;
An inner ring having a conical track surface on the outer peripheral surface;
A plurality of truncated cone-shaped rollers disposed between the outer ring and the inner ring so as to be freely rollable;
A hook that is formed on the outer ring or the outer ring and that contacts the large-diameter end surface of the roller to guide the roller,
A cage for holding the roller between the outer ring and the inner ring;
A holding member that is fitted to the outer peripheral surface of the outer ring and the inner peripheral surface of the inner ring and positions the outer ring and the inner ring at predetermined positions;
A compensating ring member engaged between the end surface of the holding member and the outer surface of the outer ring and the inner ring in the axial direction;
A tapered roller bearing disposed between structures having different coefficients of thermal expansion,
According to the present invention, the compensating ring member is made of a material having a spring force so as to compensate for the difference in thermal expansion and contraction of the structure and to maintain the setting over a wide temperature range. Rolling bearings arranged between the shaft and housing structure having different coefficients of thermal expansion, using a compensation ring, compensate for the difference in thermal expansion and contraction of the structure, and have a wide bearing setting Maintained over temperature range.

Preferably, the compensating ring member according to claim 2 is provided in a concave portion or a groove portion of the outer ring large end surface, the inner ring large end surface, the outer ring large end surface, or the front inner ring large end surface. is there.
When the compensation ring member according to a third aspect of the present invention is a disc spring or a wave spring, the magnitude of the preload can be adjusted.

The invention according to claim 4 is a housing having an abutting portion;
A shaft member that is provided in the housing and is made of a material having a coefficient of thermal expansion different from that of the material of the housing and has an abutting portion that is spaced apart and opposed to the abutting portion in the axial direction;
Having at least two tapered roller bearings for supporting the shaft member in the housing;
The tapered roller bearing is configured to receive both an axial load and a radial load, and the casing and the shaft member are opposite to each other between the abutting portions of the casing and the shaft member. By this, the tapered roller bearing restrains the shaft member in both the axial direction and the radial direction in the housing,
The tapered roller bearing has an inner ring and an outer ring, each having an end face facing away from one of the abutting portions,
Each of the outer ring and the inner ring is provided with a raceway surface, the raceway surfaces are opposed to each other,
In the bearing device in which the compensation ring member is provided between the end face of one of the inner ring and the outer ring and the abutting portion facing the end face,
It is arranged between both end faces of the inner ring and outer ring having a compensation ring, and the compensation ring member can move relative to each other when deformed in the axial direction in response to a temperature change in the housing. Thus, the compensation ring member compensates for a thermal expansion difference and a thermal contraction difference between the shaft member and the housing.
According to the present invention, by using a metal for the compensation ring, the effect of being able to omit the conformity test with various lubricating oils can be achieved as compared with the case of using a resin material having a large thermal expansion coefficient.
Furthermore, preload adjustment by shim thickness selection required in the conventional structure is not necessary. Further, in the conventional structure, when the shafts are parallel and both the shafts are combined tapered roller bearings, the shim adjustment must be established for both shafts, and the work becomes very complicated. By simply arranging the compensation ring member, adjustment work can be saved.

The present invention compensates for the difference in thermal expansion and contraction of the structure by using a compensation ring member, and the bearing setting is maintained over a wide temperature range.
Furthermore, the compensation ring member has a shape that can generate an axial force due to a spring action in addition to a dish shape or a wave-like shape at the time of initial preload setting at room temperature. Generate preload. As the temperature rises, the housing with a larger thermal expansion coefficient than the shaft member expands in the axial direction and the radial direction, and the preload applied to the bearing decreases, but the compensation ring member deforms due to the action of the spring. Since the axial force due to is generated, it tries to maintain the necessary preload. In addition, as the temperature drops, the housing having a larger coefficient of thermal expansion than the shaft member shrinks in the axial direction and the radial direction, and the preload applied to the bearing increases, but in a certain range due to the action of the spring. It is possible to keep the preload acting on the bearing.

Furthermore, by combining a plurality of compensation ring members, the preload of the tapered roller bearing can be kept uniform over a wide temperature range.
Temporarily and suddenly a very large gear load is generated, and as a reaction force, an excessive load may be input to the bearing. In this case, the compensation ring member has a plate-like shape in a preload state. By deforming into a plate shape by a large input, the load can be released to the shaft or the housing. When the large input is released, the compensation ring member returns to a predetermined shape and can return to a predetermined preload state.

A tapered roller bearing and a bearing device according to an embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 shows an enlarged schematic longitudinal sectional view of a main part of a single-row tapered roller bearing 10 according to a first embodiment of the present invention.
In FIG. 1, a single-row tapered roller bearing 10 has an outer ring 13 in which an outer peripheral surface 13a is inserted into a stepped hole 12 of a housing (holding member) 11, an inner peripheral surface 15a, and an inner ring large end surface 15b. ) 14 and an inner ring 15 inserted and inserted. A plurality of conical rollers 18 are rotatably supported by a cage 19 between the outer ring raceway surface 16 of the outer ring 13 and the inner ring raceway surface 17 of the inner ring 15. The inner ring 15 is held by the abutment portion 20 between the shoulder portion 14a of the shaft 14 and the inner ring large end surface 15a of the inner ring 15, that is, the inner ring large end surface 15b contacts the shoulder portion 14a.
On the other hand, the outer ring large end surface 13b of the outer ring 13 is an abutting portion 22 between the shoulder 12a of the stepped hole 12 of the housing 11 and the outer ring large end surface 13b of the outer ring 13 via a compensation ring (compensation ring member) 21, that is, It is held between the shoulder 12a and the outer ring large end surface 13b. The compensating ring 21 is constituted by a disc spring or a wave spring, and has a function of compensating for a difference in thermal expansion and contraction between the housing 11 and the shaft 14, and has a step with the outer ring large end face 13b of the outer ring 13 as shown in FIG. It is held in contact with a recess 23 defined by the shoulder 12 a of the attachment hole 12.
FIG. 3 shows a deformed state of the shape of the compensation ring 21 when the single-row tapered roller bearing 10 is responsive at the time of large input or low temperature, and the compensation ring 21 is the shoulder 12a of the stepped hole 12 and the outer ring of the outer ring 13. It is in close contact with the large end face 13b.
1 to 3, the case where one compensation ring 21 is provided has been described, but a plurality of compensation rings 21 may be stacked and used as shown in FIG. By combining one or a plurality of compensation rings 21, it is possible to appropriately adjust the magnitude of the preload.

FIG. 5 shows an enlarged schematic longitudinal sectional view of a main part of a single-row tapered roller bearing 30 according to the second embodiment of the present invention. In FIG. 3, the same components as those in FIGS. 1 and 2 are shown. Are denoted by the same reference numerals, and detailed description thereof is omitted. The same shall apply hereinafter.
In the single-row tapered roller bearing 30 according to the second embodiment, the engagement state between the housing 11 and the outer ring 13 will be described, and the engagement state between the shaft 14 and the inner ring 15 will be described unless otherwise specified. This is the same as the single-row tapered roller bearing 10 according to one embodiment.
In FIG. 5, a concave portion 32 is formed on the outer peripheral surface 31 a of the outer peripheral ring large end surface 31 b of the outer ring 31, and the compensation ring 21 is disposed between the shoulder portion 12 and the concave portion 32 of the housing 11.
FIG. 6 shows an enlarged schematic longitudinal sectional view of a main part of a single-row tapered roller bearing 40 according to the third embodiment of the present invention. In FIG. 6, the outer peripheral surface 41 a of the outer ring 41 is fitted into the stepped hole 14 of the housing 11, and a protruding portion 42 extending in the diameter direction is formed on the outer ring large end surface 41 b of the outer ring 41. The compensating ring 21 is held in the abutting portion 43 between the inner side surface 42a and the end surface 11a of the holding member 11, that is, the recess 44 surrounded by the end surface 11a and the inner side surface 42a.

FIG. 7 is an enlarged schematic vertical sectional view showing a main part of a single-row tapered roller bearing 50 according to the fourth embodiment of the present invention. In FIG. 7, outer peripheral surfaces 55 a and 55 b of an outer ring 55 are fitted and inserted into the small diameter hole 53 and the large diameter hole 54 of the stepped hole 52 of the housing 51. A protrusion 56 extending in the diameter direction is formed on the outer ring large end surface 55c of the outer ring 55, and constitutes an outer peripheral surface 55b.
Further, the compensating ring 21 is held in the abutting portion 57 between the end surface 51a and the inner surface 56a of the protrusion 56, that is, the groove portion 58 formed with the end surface 51a and the inner surface 56a.
FIG. 8 shows an enlarged schematic longitudinal sectional view of a main part of a single row tapered roller bearing 60 according to the fifth embodiment of the present invention. In the single-row tapered roller bearing 60, the engagement state between the shaft 14 and the inner peripheral surface 15a of the inner ring 15 shown in FIG. 1 will be described, and the engagement state between the housing 11 and the outer ring 13 is shown in FIGS. This is the same as the single-row tapered roller bearing 10 according to the first embodiment.

In FIG. 8, the compensation ring 21 is held in the shoulder portion 14a of the shaft 14, the inner ring large end surface 15b of the inner ring 15 and the abutting portion 61, that is, the recess 62 surrounded by the shoulder portion 14a and the inner ring large end surface 15b. .
FIG. 9 is an enlarged schematic longitudinal sectional view of the main part of a single row tapered roller bearing 70 according to the sixth embodiment of the present invention. In FIG. 9, a concave portion 71 is formed on the inner ring large end surface 15 b of the inner ring 15, and the compensation ring 21 is held between the shoulder portion 14 a of the shaft 14 that forms the abutting portion 72 and the concave portion 71.
In the single-row tapered roller bearings 10, 30, 40, 50, 60, and 70 according to the embodiment of the present invention, it is possible to adjust the magnitude of the preload by combining one or a plurality of compensation rings 21. Become.
The compensating ring 21 is preferably disposed on one or both of the combined tapered roller bearings, and is preferably inserted into the outer ring large end surface or the inner ring large end surface of the bearing not subjected to the thrust load.
In the embodiment of the present invention, the single-row tapered roller bearing has been described. However, it can be applied to a single-row angular contact ball bearing.

Next, the case where the single row tapered roller bearing according to the embodiment of the present invention is applied to an automobile transmission will be described. FIG. 10 is a schematic longitudinal sectional view of a bearing device 80 in which a single-row tapered roller bearing 60 according to the fifth embodiment is applied to a manual transmission 75.
In FIG. 10, the manual transmission 75 includes a casing 81 cast from a lightweight metal such as an aluminum alloy or a magnesium alloy. The manual transmission 80 includes an input shaft (shaft member) 83 aligned in the axial direction along the rotation axis X, and an output shaft 84 along another rotation axis Y substantially parallel to the rotation axis X. With.
As a result, the input shaft 83 and the output shaft 84 are all provided with a plurality of gears 85a to 85f and 86a to 86e that mesh with different combinations that generate a differential speed ratio between the input shaft 83 and the output shaft 84. Established.

The input shaft 83 is pivotally supported by a single row cylindrical roller bearing 88 disposed on a housing 82 joined to the housing 81 by a screw member 87 on one side, and disposed on the opposite end wall of the housing 81. It is supported by a single row ball bearing 89.
The output shaft 84 is accommodated in the casing 81, and ends thereof are respectively provided in the holes 90 and 91 located on the side wall of the casing 81 in the single-row tapered roller bearing 10 (see FIG. 1) and a normal single-row tapered cone. A roller bearing 92 is received. As shown in FIGS. 11A and 11B, the output shaft 84 is a shaft portion thereof, and has shoulder portions 93 and 94, and the single row tapered roller bearings 10 and 92 have the shoulder portions 93, 94 and It is held between shoulders 95 and 96 formed at the ends of the holes 90 and 91 of the casing 81. In this case, the shoulder portions 93, 94, the outer ring large end surface 15 b of the inner ring 15, and the inner ring large end surface 105 a of the inner ring 105 form abutting portions 97, 98. The shoulder portions 95 and 96, the outer ring large end surface 13 b of the outer ring 13, and the outer ring large end surface 103 b of the outer ring 103 form abutting portions 99 and 100.
The single row tapered roller bearings 10 and 92 prevent them from moving the output shaft 84 in the diametrical direction or the axial direction in the housing 81, and further, they can rotate the output shaft 84 with a minimum frictional resistance. Therefore, the output shaft 84 is held in the housing 81. The shoulder portions 93 and 94 function as end surfaces of the gears 85a and 85f, respectively.

  As shown in FIG. 11A, in the single-row tapered roller bearing 10, the outer ring 13 is inserted into the hole 90 of the casing 81, and the compensating ring 21 (see FIG. 1) is provided between the outer ring large end face 13b and the shoulder portion 95. The inner ring 15 is fitted to the shaft end portion 102 of the output shaft 84, and the inner ring large end surface 15a is engaged with the shoulder portion 95, that is, the end surface of the gear 85a. As shown in FIG. 11B, in the single-row tapered roller bearing 92, the outer ring 103 is fitted in the hole 91 of the housing 81, the outer ring large end surface 103b engages with the shoulder portion 96, and the inner ring 105 is connected to the output shaft 84. The inner ring large end surface 105b is engaged with the shoulder portion 94, that is, the end surface of the gear 85f. The compensating ring 21 is preferably disposed on one or both of the bearings 10 and 92 constituting the combined tapered roller bearing. In the bearing device 80 according to this embodiment, the compensation ring 21 is held in the recess 23 (see FIG. 2) defined by the outer ring large end surface 13b of the outer ring 13 and the shoulder 95 of the single row tapered roller bearing 10. .

In the bearing device 80 shown in FIG. 10, the housing 81 having a larger coefficient of thermal expansion than the input shaft 83 and the output shaft 84 expands in the axial direction and the radial direction as the temperature increases due to the operation of the manual transmission 75. Although the preload applied to the tapered roller bearings 10 and 92 decreases, an axial force is generated by the deformation of the compensation ring 21 due to the action of the spring, so that the necessary preload is maintained. As the temperature drops, the casing 81 having a thermal expansion coefficient larger than that of the input shaft 83 and the output shaft 84 contracts in the axial direction and the radial direction, and the preload applied to the single row tapered roller bearings 10 and 92 increases. However, the preload can be continuously applied to the bearing within a certain range by the spring action of the compensation ring 21.
According to this configuration, it is possible to adjust the magnitude of the preload by combining one or a plurality of compensation rings.
In the bearing device 80, the case where the single-row tapered roller bearing 60 according to the fifth embodiment is applied to the manual transmission 75 has been described. However, the single-row cone according to the first to fourth and sixth embodiments is described. Of course, it is also possible to employ the roller bearings 10, 30, 40, 60, 70.

It is a principal part expansion schematic longitudinal cross-sectional view of the single row tapered roller bearing concerning 1st embodiment of this invention. 2 is an enlarged schematic longitudinal sectional view showing an engagement state between an outer ring and a compensation ring in FIG. 1. 2 is an enlarged schematic longitudinal cross-sectional view showing a state where an outer ring and a compensation ring in FIG. 1 are in close contact with each other. FIG. 2 is an enlarged schematic longitudinal sectional view showing a stacked state of the compensation ring of FIG. It is a principal part expansion schematic longitudinal cross-sectional view of the single row tapered roller bearing concerning 2nd embodiment of this invention. It is a principal part expansion schematic longitudinal cross-sectional view of the single row tapered roller bearing concerning 3rd embodiment of this invention. It is a principal part expanded schematic longitudinal cross-sectional view of the single row tapered roller bearing concerning 4th Embodiment of this invention. It is a principal part expansion schematic longitudinal cross-sectional view of the single row tapered roller bearing concerning the 5th Embodiment of this invention. It is a principal part expansion schematic longitudinal cross-sectional view of the single row tapered roller bearing concerning the 6th Embodiment of this invention. It is a schematic longitudinal cross-sectional view of the bearing apparatus which employ | adopted the single row tapered roller bearing for the manual transmission. It is a schematic longitudinal cross-sectional view which shows the engagement state of the single row tapered roller bearing of FIG. 10, and an output shaft.

Explanation of symbols

10, 20, 40, 50, 60, 70, 92 Single row tapered roller bearings 11, 51 Housing 12, 52 Stepped holes 13, 41, 103 Outer ring 14 Shafts 12a, 14a, 93 to 96 Shoulders 15, 105 Inner ring 16 Outer ring raceway surface 17 Inner ring raceway surface 18 Conical roller 20, 22, 43, 57, 61, 72, 99, 100 Abutting portion 21 Compensation ring 23, 43, 64, 71 Recessed portion 42 Protruding portion 80 Bearing device 81 Housing 83 Input Shaft 84 Output shaft 85, 86 Gear 101 Housing 102, 104 Shaft end

Claims (4)

An outer ring having a conical track surface on the inner peripheral surface;
An inner ring having a conical track surface on the outer peripheral surface;
A plurality of truncated cone-shaped rollers disposed between the outer ring and the inner ring so as to be freely rollable;
A hook that is formed on the outer ring or the outer ring and that contacts the large-diameter end surface of the roller to guide the roller,
A cage for holding the roller between the outer ring and the inner ring;
A holding member that is fitted to the outer peripheral surface of the outer ring and the inner peripheral surface of the inner ring and positions the outer ring and the inner ring at predetermined positions;
A compensating ring member engaged between the end surface of the holding member and the outer surface of the outer ring and the inner ring in the axial direction;
A tapered roller bearing disposed between structures having different coefficients of thermal expansion,
A tapered roller bearing, wherein the compensating ring member is made of a material having a spring force so as to compensate for a difference in thermal expansion and contraction of the structure and to maintain the setting over a wide temperature range. The tapered roller bearing according to claim 1,
The tapered ring bearing is characterized in that the compensating ring member is provided in a concave portion or a groove portion of the outer ring large end surface or the inner ring large end surface, the outer ring large end surface or the front inner ring large end surface. The tapered roller bearing according to claim 1 or 2,
A tapered roller bearing, wherein the compensating ring is a disc spring or a wave spring. A housing having an abutting portion;
A shaft member that is provided in the housing and is made of a material having a coefficient of thermal expansion different from that of the material of the housing and has an abutting portion that is spaced apart and opposed to the abutting portion in the axial direction;
Having at least two tapered roller bearings for supporting the shaft member in the housing;
The tapered roller bearing is configured to receive both an axial load and a radial load, and the casing and the shaft member are opposite to each other between the abutting portions of the casing and the shaft member. By this, the tapered roller bearing restrains the shaft member in both the axial direction and the radial direction in the housing,
The tapered roller bearing has an inner ring and an outer ring, each having an end face facing away from one of the abutting portions,
Each of the outer ring and the inner ring is provided with a raceway surface, the raceway surfaces are opposed to each other,
In the bearing device in which the compensation ring member is provided between the end face of one of the inner ring and the outer ring and the abutting portion facing the end face,
It is arranged between both end faces of the inner ring and the outer ring having a compensation ring member, and the compensation ring member can move relative to each other when deformed in the axial direction in response to a temperature change in the housing, Thereby, the compensation ring member compensates for a thermal expansion difference and a thermal contraction difference between the shaft member and the housing.

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