JP2006234098A - Bearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing device reduced in the quantity of parts, simplified in structure, and enabling the easy adjustment of the preload and the axial clearance of a bearing. <P>SOLUTION: This bearing device comprises a single inner ring 1 in which two rows of inner ring raceways are formed on its outer peripheral surface, a pair of outer rings 2 and 3 installed with clearances in the axial direction and having one-row outer ring raceways formed on their inner peripheral surfaces, and rolling elements 4 and 5 rollingly interposed between the inner ring raceway and the outer ring raceways. Also, a spacer 6 is installed between the pair of outer rings 2 and 3. Outer ring tilted surfaces 2b and 3b are formed on the spacer 6 side axial end faces of the outer rings 2 and 3. A spacer tilted surface 14 brought into contact with the outer ring tilted surfaces 2b and 3b and pressing the outer rings 2 and 3 to the axial both sides to impart a preload thereon is formed on the spacer 6. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a bearing device.

A turbocharger of an automobile has a turbine wheel attached to one end of a rotating shaft, a compressor wheel attached to the other end, and an intermediate portion of the rotating shaft is inserted through a hole in a housing of the turbocharger. The rotating shaft is rotatably supported by the bearing device.
And what is conventionally known as such a bearing device, as shown in Patent Document 1 and Patent Document 2, single-row angular contact ball bearings are arranged on both sides of the rotating shaft, respectively, and between these angular contact balls, Some are provided with a coil spring that elastically biases the outer ring of the bearing toward both sides in the axial direction and a C-shaped spacer.

JP 11-101128 A Utility Model Registration No. 2577011

  However, such a conventional bearing device has a problem that the number of parts is large, the structure is complicated, the number of assembling steps is increased, and the cost is increased. Assembling this bearing device requires mounting the angular ball bearing on one axial side in a predetermined position, providing a coil spring and a spacer, and mounting the angular ball bearing on the other axial side. Therefore, in order to facilitate the assembly, it is conceivable to manufacture the bearing device by integrating it in advance and attach it to the hole of the turbocharger housing. However, in the case of this integrated bearing device, it becomes difficult to adjust and manage the preload of the bearing portion and the axial gap.

  In other words, the turbocharger has a rotating shaft that rotates at a high speed of several tens of thousands of revolutions / minute. Preload is added. Accordingly, in assembling the turbocharger, it is necessary to adjust and manage the preload and the axial gap of the bearing portion. In the conventional bearing device, this preload is given by a coil spring, but since a sleeve is provided radially outward of the coil spring, once the bearing device is assembled, the work for adjusting the preload by the coil spring is performed. There is a problem that the work of exchanging the is very difficult.

  Therefore, the present invention has been made in view of the above problems, and provides a bearing device that can reduce the number of parts and simplify the structure, and can easily adjust the preload and the axial gap of the bearing. Objective.

  In order to achieve the above object, a bearing device of the present invention includes a single inner ring having two rows of inner ring raceways formed on the outer peripheral surface, and one row of outer rings provided on the inner peripheral surface with an interval in the axial direction. A pair of outer rings each formed with a track, a rolling element interposed between the inner ring track and the outer ring track, and a spacer provided between the pair of outer rings, At least one of the pair of outer rings has an outer ring inclined surface formed on an end surface in the axial direction on the spacer side, and the spacer is in contact with the inclined surface of the outer ring and presses the outer ring toward both sides in the axial direction to apply preload. A spacer inclined surface to be applied is formed.

According to the bearing device having such a configuration, the spacer can press the pair of outer rings to both sides in the axial direction where the outer rings are separated from each other, and the preload is applied to the bearing portions on both axial sides constituted by the outer ring, the rolling element, and the inner ring. Further, fine adjustment of the axial gap of the bearing portion is facilitated.
In other words, since the pressing surface of the spacer that presses the inclined surface of the outer ring of the outer ring is an inclined surface, it is easy to preload by moving at least one outer ring in the axial direction by adjusting the position of the spacer in the radial direction. Strength and axial gap can be adjusted. Furthermore, since the spacer applies a preload to the bearing portion and adjusts the axial gap, a means for applying a preload or the like is not necessary, and the number of parts can be reduced.
Further, since the inner ring is a single member, the number of parts can be reduced, and the bearing device can be integrated, so that the bearing device can be easily mounted. That is, the two rows of rolling elements, the pair of outer rings, and the spacer can be assembled in advance to the inner ring, and the bearing device can be easily attached to the mounting portion of the bearing device.

  Further, the spacer is preferably an arc member centered on the bearing axis, and the spacer is preferably provided at a plurality of locations in the circumferential direction. According to this configuration, the spacer can press the outer ring in the axial direction from a plurality of locations in the circumferential direction, and the spacer is an arc-shaped member along the circumferential shape of the outer ring. A uniform pressing force in the direction can be applied to the outer ring.

  Moreover, it is preferable to have a position adjusting means for moving the spacer in the radial direction. According to this configuration, the bearing preload and the axial gap can be easily adjusted by moving the spacer in the radial direction.

  The bearing device is a turbocharger bearing that is mounted in a hole of a housing and rotatably supports a rotating shaft. Thereby, the number of parts is reduced, the configuration is simplified, and the bearing device can be easily mounted on the housing of the turbocharger. In addition, this bearing device that supports a rotating shaft that rotates at a high speed and whose rotational speed fluctuates greatly can be simply and appropriately applied with a preload, the axial gap can be adjusted, and the rotational accuracy of the rotating shaft can be improved. it can.

  According to the bearing device of the present invention, the number of parts can be reduced, the structure can be simplified, the assembly is easy, and the cost can be reduced. Also, preload and axial clearance can be easily adjusted and managed.

Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 is a longitudinal sectional view showing a bearing device according to an embodiment of the present invention. This bearing device can rotatably support the rotating shaft 12 in a through hole 13 formed in the housing H, and is a double row bearing having two rows of rolling elements 4 and 5 in the axial direction. Device. As a device using such a bearing device, there is a turbocharger of an automobile.

This bearing device includes a single inner ring 1 that is externally fitted to a rotary shaft 12, a pair of outer rings 2 and 3 that are provided radially outward of the inner ring 1, and a space between the inner ring 1 and the outer rings 2 and 3. Two rows of rolling elements 4, 5 provided in a freely rotatable manner in the annular space, and a spacer 6 provided between the pair of outer rings 2, 3.
This bearing device is provided in the hole 13 of the housing H, and a pair of outer rings 2 and 3 provided with a spacer 6 between them are formed by a stepped surface 15 of the hole 13 of the housing H and a disc. The one end surface 1a in the axial direction of the inner ring 1 is in contact with a cylindrical spacer 17 that is provided on the outer peripheral side of the rotary shaft 12 and whose position is restricted in the axial direction. Yes. That is, the bearing device is mounted in the hole 13 of the housing H in the axial direction by the retaining ring member 16 and the cylindrical spacer 17 provided so as to sandwich the bearing device from both sides in the axial direction.

The inner ring 1 in which two rows of inner ring raceways 7 and 8 are formed on the outer peripheral surface is configured as a cylindrical part (integrated one). The inner ring raceways 7 and 8 of the inner ring 1 are circumferential grooves formed with a predetermined radius of curvature in angular contact with the balls constituting the rolling elements 4 and 5.
The first outer ring 2 on one side in the axial direction is a cylindrical member, and a single outer ring raceway 9 is formed so as to face the first inner ring raceway 7 formed on the inner ring 1. A first rolling element 4 is provided between the inner ring raceway 7 and the outer ring raceway 9. The outer ring raceway 9 is a circumferential groove formed with a predetermined radius of curvature, and is formed on the inner circumferential surface of the outer ring 2 so as to make an angular contact with the balls constituting the rolling element 4.
Similarly, the second outer ring 3 on the other side is also a cylindrical member, and a single outer ring raceway 10 is formed so as to face the second inner ring raceway 8 formed on the inner ring 1. An outer ring raceway 10 is formed so as to make angular contact with the balls constituting the second rolling element 5. This bearing device has a structure in which the inner ring 1 is integrated and the outer rings 2 and 3 are divided to form a double-row angular ball bearing.

  The bearing device shown in FIG. 1 has, in a cross section passing through the shaft center, a straight line connecting a contact point between the ball of the rolling element 4 on one side in the axial direction and the inner ring raceway 7 and the outer ring raceway 9, and the other side in the axial direction. The balls on both sides are the inner ring 1 and the outer rings 2, 3 so that the straight line connecting the contact points of the balls of the moving body 5 and the inner ring raceway 8 and the outer ring raceway 10 intersects radially outward of the outer rings 2, 3. It is set as the structure which makes an angular contact.

  The pair of outer rings 2, 3 are provided concentrically with the inner ring 1 on the outer peripheral side of the inner ring 1 with an interval in the axial direction, and a spacer 6 is provided between the pair of outer rings 2, 3. As shown in FIG. 1, the cross-sectional shape of the spacer 6 is a trapezoid in which the short side of the two parallel sides is the radially inner side and the long side is the radially outer side, and the width dimension toward the center. The wedge is reduced. As shown in FIG. 2, the spacer 6 is an arc-shaped member centered on the bearing axis when viewed in the axial direction. Accordingly, the side surface of the spacer 6 is an inclined surface (tapered surface) 14 that is inclined at a predetermined angle with respect to a surface orthogonal to the axial center. In FIG. 1, both side surfaces are inclined surfaces 14a and 14b. ing.

An outer ring inclined surface 2b is formed on the inner end surface in the axial direction of the outer ring 2, that is, on the axial end surface on the spacer 6 side, and is directed toward the outer ring 3 on the other side toward the center. The inclined surface to be pressed is inclined at the same angle as the inclined surface 14 a of the seat 6. Similarly, in the outer ring 3, an outer ring inclined surface 3 b is formed on the axial end surface on the spacer 6 side, and the outer ring inclined surface 3 b is a pressed inclined surface inclined at the same angle as the inclined surface 14 b of the spacer 6. Has been. Therefore, the width of the annular space between the outer rings 2 and 3 increases radially outward.
The inclined surface 14a of the spacer 6 is in contact with the outer ring inclined surface 2b of the outer ring 2, and presses the outer ring 2 outward in the axial direction. Similarly, in the outer ring 3 on the opposite side, the inclined surface 14b of the spacer 6 is in contact with the outer ring inclined surface 3b of the outer ring 3 and presses the outer ring 3 outward in the axial direction. That is, the spacer 6 disposed between the pair of outer rings 2 and 3 presses the outer rings 2 and 3 toward both sides in the axial direction, which is the direction in which the outer rings 2 and 3 are separated from each other, by the inclined surfaces 14a and 14b.

  In the embodiment of FIG. 1, the inclined surfaces 14 a and 14 b are formed on both sides in the axial direction of the spacer 6. And the other side surface is a surface orthogonal to the axial direction, and a corresponding inclined surface is formed on the axial end surface of the outer ring that contacts the inclined surface formed on the spacer 6. Good. Even in this case, by adjusting the position of the spacer 6 in the radial direction, both the left and right outer rings 2 and 3 can be moved in the axial direction, and the strength of the preload and the axial gap can be adjusted.

As shown in FIG. 2, the spacer 6 is an arc member centered on the bearing axis, and the spacer 6 is provided at a plurality of locations in the circumferential direction. For example, the spacer 6 is an arc member having a central angle of 90 °, and the two spacers 6 and 6 are separated by 180 ° about the bearing axis in the space between the outer rings 2 and 3. It is arranged to face each other. Although the number of the spacers 6 is plural, the number thereof is not limited, and the plural spacers 6 are preferably arranged at equal intervals in the circumferential direction around the bearing shaft center.
Thereby, the plurality of spacers 6 can press the outer rings 2 and 3 evenly in the circumferential direction from a plurality of locations in the circumferential direction, and the spacers 6 are arcs along the circumferential shape of the outer rings 2 and 3. Since the member is shaped, a uniform pressing force in the circumferential direction can be applied to the outer rings 2 and 3.

The spacer 6 is held in the radial position by the outer peripheral surface thereof coming into contact with the inner peripheral surface of the hole 13 of the housing H. Therefore, the outer peripheral surface of the spacer 6 is an arc surface that comes into contact with the inner peripheral surface of the hole 13, and it is preferable that this arc surface has (substantially) the same radius of curvature as the inner peripheral surface of the hole 13. Note that the outer peripheral surface shape and the radius of curvature of the spacer 6 are such that the inclined surfaces 14 and 14 of the spacer 6 press the outer ring inclined surfaces 2b and 3b while the bearing device is fitted in the hole 13 of the housing H. It is set to give a predetermined preload and an axial gap to the part.
Therefore, before the bearing device is assembled in the housing H, it is possible to set the preload to be applied to the bearing portion. This increases the production efficiency and enables mass production.
Further, the operation of weakening the pressing force on the outer rings 2 and 3 can adjust the pressing force on the outer ring inclined surfaces 2 b and 3 b of the outer rings 2 and 3 by cutting the inclined surface 14 of the spacer 6.
Further, the inclination angle of the spacer 6 with respect to the inclined surface 14 and the surfaces of the outer rings 2, 3 perpendicular to the axis of the outer ring inclined surfaces 2b, 3b is an angle at which the spacer 6 does not come out radially outward due to friction between them. For example, it can be about 7 °. As a result, the spacer 6 presses the pair of outer rings 2 and 3 toward both sides in the axial direction, and the spacer 6 is held in the radial position by friction on the inclined surface 14.

  For example, the inner ring 1 and the outer ring 2 are manufactured by deep drawing a steel plate such as a cold rolled steel plate to form a track so as to have a predetermined radius of curvature, and then performing a heat treatment such as carburizing quenching and induction quenching. Can do. Also. The balls of the rolling elements 4 and 5 are made of a steel material such as stainless steel, and are arranged at predetermined intervals in the circumferential direction by a cage not shown. The spacer 6 can be made of the same (same) material as the inner ring 1 and the outer ring 2.

  As described above, in this bearing device, the outer ring inclined surfaces 2b and 3b are formed on the axial end surface on the spacer 6 side in each of the pair of outer rings 2 and 3, and the spacer 6 has this Since the inclined surface 14 is formed to contact the outer ring inclined surfaces 2b and 3b and press the outer rings 2 and 3 axially on both sides, the outer ring 2 and 3 is axially adjusted by adjusting the position of the spacer 6 in the radial direction. It is possible to easily apply a preload to both bearing portions. Further, the strength of the preload and the axial gap can be easily adjusted.

The bearing device described above is suitable as a turbocharger bearing that is mounted in the hole 13 of the housing H and rotatably supports the rotary shaft 12. That is, although not shown, a turbine wheel is attached to one end of the rotating shaft 12, a compressor wheel is attached to the other end, and an intermediate portion of the rotating shaft 12 is inserted through the hole 13 of the housing H of the turbocharger. The inner ring 1 of the bearing device is externally fitted to the intermediate portion, and the outer rings 2 and 3 of the bearing device are provided on the inner peripheral surface side of the hole 13.
A minute gap constituting an oil fill damper is formed between the outer peripheral surfaces of the outer rings 2 and 3 and the inner peripheral surface of the hole 13. Then, lubricating oil is supplied to the gap via an oil supply hole (not shown) formed in the housing H, and this lubricating oil functions as a damper that attenuates vibration of the rotating shaft 12.

Therefore, by using the bearing device as a turbocharger bearing, the spacer 6 applies a preload to the bearing portion and adjusts the axial gap, so that a means for separately applying a preload or the like is not required. Since 1 is a single member, the number of parts can be reduced. And this bearing apparatus can be integrated previously, and mounting | wearing of the bearing apparatus to the housing H of a turbocharger becomes easy.
In addition, a preload can be easily and appropriately applied to the bearing device that supports the rotating shaft 12 that rotates at a high speed and the number of rotations fluctuates greatly, and the axial gap can be adjusted, thereby improving the rotation accuracy of the rotating shaft 12. be able to.

  FIG. 3 is a longitudinal sectional view showing another embodiment of the bearing device of the present invention, and this bearing device has a position adjusting means 11 for moving the spacer 6 in the radial direction. If the operation unit is provided outside the housing H in which the bearing device is incorporated, the position adjusting means 11 can preload the bearing unit without being disassembled even after the bearing device is mounted in the hole 13 of the housing H. The axial gap can be changed and adjusted. In the bearing device of FIG. 3, the same components as those shown in the bearing device of FIG.

The specific configuration of the position adjusting means 11 is, for example, as shown in FIG. 3, in which a linear through hole 18 that penetrates the meat part of the housing H from the outer surface of the housing H and opens to the hole part 13 is formed. A screw rod 19 is inserted into the through-hole 18, a distal end surface of the spacer 6 abuts on the outer peripheral surface of the spacer 6, and a base end portion projects from the outer surface of the housing H. The screw rod 19 is arranged so that the radial direction around the axis of the bearing device is the longitudinal direction. The screw rod 18 is screwed into a nut portion 20 provided in the housing H, and the screw rod 18 moves the nut portion 20 forward and backward, whereby the spacer 6 can be moved in the radial direction. That is, when the screw rod 18 is advanced and pressed toward the center 6 toward the center, the pair of outer rings 2 and 3 are pressed away from each other and preload is applied to the bearing portion.
In addition, at least one position adjusting means 11 is provided for one spacer 6, but a plurality of the position adjusting means 11 are provided for one spacer 6 to press the spacer 6 from a plurality of locations in the circumferential direction. preferable.

  According to this position adjusting means 11, if the operating portion (head of the screw rod 18) of the position adjusting means 11 is provided outside the housing H in which the bearing device is incorporated, the bearing device is placed in the hole 13 of the housing H. Even after the mounting, the preload and the axial gap of the bearing portion can be changed and adjusted from the outside of the housing H without being disassembled.

  Although the bearing device of the present invention is not shown, the outer ring 2 (outer ring 3) may have a divided structure. In other words, the outer ring main body having the outer ring raceway 9 (10) and an annular outer member attached to the outer ring main body may be used. That is, the outer ring main body can be an off-the-shelf standard specification product, and the product cost can be reduced.

  Further, the bearing device of the present invention is not limited to the illustrated form, and may be of other forms within the scope of the present invention. Inner ring raceways 7 and 8 are formed on the outer peripheral surface of the rotating shaft 12, and the rotating shaft The outer periphery of 12 may be the inner ring 1.

It is a longitudinal cross-sectional view which shows one Embodiment of the bearing apparatus of this invention. It is the figure which looked at the spacer from the axial direction. It is a longitudinal cross-sectional view which shows other embodiment of a bearing apparatus.

Explanation of symbols

Reference Signs List 1 inner ring 2 first outer ring 2b outer ring inclined surface 3 second outer ring 3b outer ring inclined surface 4 first rolling element 5 second rolling element 6 spacer 7 first inner ring race 8 second inner ring race 9 first Outer ring raceway 10 Second outer ring raceway 11 Position adjusting means 12 Rotating shaft 13 Hole 14 Spacer inclined surface H Housing

Claims (4)

  A single inner ring in which two rows of inner ring raceways are formed on the outer peripheral surface, a pair of outer rings that are provided at intervals in the axial direction and in which one row of outer ring raceways are formed on the inner peripheral surface, and the inner ring raceways A rolling element interposed between the outer ring raceway and the outer ring raceway, and a spacer provided between the pair of outer rings, and at least one of the pair of outer rings includes the spacer side The outer ring inclined surface is formed on the axial end surface of the outer ring, and the spacer is formed with a spacer inclined surface that abuts against the outer ring inclined surface and presses the outer ring axially on both sides to apply preload. A bearing device.   The bearing device according to claim 1, wherein the spacer is an arc member centered on a bearing axis, and the spacer is provided at a plurality of locations in a circumferential direction.   The bearing device according to claim 1, further comprising a position adjusting unit that moves the spacer in a radial direction.   The bearing device according to claim 1, wherein the bearing device is a turbocharger bearing that is mounted in a hole portion of the housing and rotatably supports the rotating shaft.

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