JP2005265099A - Double row ball bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a double row ball bearing miniaturizing and lightening a transmission and preventing creep. <P>SOLUTION: The double row ball bearing 1 is provided with an inner ring 2 including double raceway grooves on an outer circumference surface, a pair of outer rings 3, 3 including single raceway groove on an inner circumference surface, a plurality of balls 4 arranged in double rows between the inner ring and a pair of the outer rings 3, 3 and a pair of resin retainers 5, 5 retaining balls 4 of each row with keeping equal interval in a circumference direction. A projection part 12 provided on an outer circumference surface of the retainer 5 is engaged with a groove part 13 provided on the inner circumference surface of the outer ring 3. An annular member 9 for preventing creep of the inner ring 2 is installed on the annular groove 8 provided on an inner circumference surface of the inner ring 2. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a double row ball bearing, and more particularly to a double row ball bearing used in a transmission such as an automobile transmission, an automatic transmission, a belt CVT, or a transfer.

  For example, a transmission used in an automobile or the like has a gear for transmitting power from an engine, and a load generated by the meshing of the gear is loaded on a bearing via a rotating shaft. As a bearing that applies such a load and smoothly supports the rotation of the shaft, a double-row ball bearing of a rear combination type has been widely put into practical use.

  As shown in FIG. 4, the double-row ball bearing 100 of the back combination type includes a pair of inner rings 101 and 101 each having one row of raceway grooves on the outer peripheral surface, and an outer ring 102 having two rows of raceway grooves on the inner peripheral surface. A plurality of balls 103 arranged in a double row between the raceway grooves of the pair of inner rings 101, 101 and the outer ring 102, and a pair of cages 104 that hold the balls 103 in each row at equal intervals in the circumferential direction. , 104.

  The outer ring 102 is fixed to the housing 106 by being positioned by a retaining ring 105. In addition, the pair of inner rings 101, 101 is to be separated from the double row ball bearing 100 by the axial component force generated when the double row ball bearing 100 applies a radial load. It is fixed to the rotating shaft 108 and an appropriate preload is applied. As described above, by using the double row ball bearing 100 having the pair of inner rings 101, 101, the transmission is reduced in size and weight.

  In addition, there is known a rolling bearing in which a protrusion is provided on the cage so that the outer ring or the inner ring and the cage are not separated (see, for example, Patent Document 1), and the double row ball bearing shown in FIG. Also in 100, the cages 104, 104 have protrusions 109, 109 that engage with the inner rings 101, 101 so that the cages 104, 104 are not separated from the inner rings 101, 101 during assembly work or disassembly work.

  Also, in rolling bearings, there are cases where gaps occur on the mating surfaces of the bearings due to thermal expansion due to heat generation or eccentricity with the counterpart machine, and creep occurs. Has been proposed (see, for example, Patent Documents 2 to 4).

  In the creep prevention device described in Patent Document 2, an eccentric ring made of synthetic resin having elasticity is mounted in an eccentric groove formed on an outer peripheral surface of an outer ring constituting a rolling bearing. The partial outer circumferential surface of the eccentric ring is in wide contact with the partial inner circumferential surface of the housing, thereby preventing the outer ring creep.

  In the creep prevention device described in Patent Document 3, the elastic body is mounted in a storage groove formed in the circumferential direction of at least one peripheral surface of the outer ring or the housing constituting the rolling bearing, and the other peripheral surface The outer ring creep is prevented from occurring by bulging into a recess formed in the outer surface.

In the creep prevention device described in Patent Document 4, the housing and the outer ring are made of materials having different thermal expansion coefficients, and a plurality of members in which at least one of the housing and the shaft is separate from each other are arranged in series in the axial direction. Thus, an O-ring is attached to the outer diameter of the outer ring to prevent the occurrence of outer ring creep.
U.S. Pat. No. 3,649,094 (column 1-3, Fig. 1-3) JP-A-10-82428 (Section 3-5, Fig. 1-2) JP-A-10-299785 (Section 2-4, Fig. 2-3) Japanese Patent Laid-Open No. 2001-27255 (Section 3-4, Fig. 1-3)

  By the way, the rotating shaft 108 normally used in the transmission has a shaft diameter of about φ20 to φ50 in order to transmit power from the engine. Therefore, the name of the nut 107 used for fixing the inner rings 101, 101 to the rotary shaft 108 and applying an appropriate preload is M20 to M50, and a large nut is required. For this reason, depending on the design of the transmission, the use of a back-row combination double row ball bearing may be abandoned because there is no space for the nut 107 in the housing 106.

  In many cases, the outer ring 102 of the double-row ball bearing 100 of the back combination type is usually used by being fixed to a housing 106 with a retaining ring 105. In this case, the housing 106 and the outer ring 102 are in a so-called mating state. Thus, when disassembling, it is difficult to remove the double row ball bearing 100 from the housing 106, and there is a problem that both the housing 106 and the double row ball bearing 100 cannot be reused.

Furthermore, in order to prevent the creep of the double row ball bearing 100, even if the anti-creep device described in Patent Documents 2 to 4 is used, the above problem cannot be solved.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a double row ball bearing capable of reducing the size and weight of a transmission and preventing creep. It is in.

The above-mentioned subject concerning the present invention is attained by the following composition.
(1) Front combination between the inner races having two rows of raceway grooves on the outer peripheral surface, a pair of outer races each having one row of raceway grooves on the inner circumference surface, and both raceway grooves of the inner race and the pair of outer races A plurality of balls arranged in double rows, and a pair of resin cages that hold the balls in each row at equal intervals in the circumferential direction,
The retainer is attached to the outer ring by engaging a protrusion provided on the outer peripheral surface thereof with a groove provided on the inner peripheral surface of the outer ring,
A groove (annular groove in this embodiment) is formed in the inner ring of the inner ring, and a member (annular member in the present embodiment) for preventing creep of the inner ring is formed in the groove. A double-row ball bearing characterized by being mounted.
(2) Each said outer ring is a counterbore type,
The cage includes a large-diameter side annular portion facing the inner peripheral surface of the outer ring on the counterbore side, and a small-diameter side annular portion facing the inner peripheral surface on the counter-counter side,
The protrusion is formed on the outer peripheral surface of the large-diameter side annular portion, and the groove is provided on the inner peripheral surface of the outer ring on the counter bore side. Row ball bearing.
(3) The double row ball bearing according to (1) or (2), wherein the member is any one of an O-ring, a resin member, and a metal member.
(4) The double-row ball bearing according to any one of (1) to (3), wherein the outer ring includes a notch on the outer peripheral surface on the counter-counter bore side.

  According to the double row ball bearing of the present invention, both races of an inner ring having two rows of raceway grooves on the outer peripheral surface, a pair of outer rings each having one row of raceway grooves on the inner peripheral surface, and an inner ring and a pair of outer rings. The double row ball bearing is provided with a plurality of balls arranged in a double row in front combination between the grooves and a pair of resin cages that hold the balls in each row at equal intervals in the circumferential direction. Therefore, a large nut is not required to apply the preload to the inner ring. Therefore, the space for the nut can be saved, and the transmission can be reduced in size and weight.

  Further, since the retainer is mounted on the outer ring by engaging the protrusion provided on the outer peripheral surface thereof with the groove provided on the inner peripheral surface of the outer ring, when performing disassembly, the retainer and the outer ring Can be easily prevented. Furthermore, a member for preventing creep of the inner ring is attached to the groove formed in the inner peripheral surface of the inner ring, and creep that occurs between the inner ring and the rotating shaft can be prevented.

  By using the double row ball bearing of the present invention, it is possible to provide a double row ball bearing capable of reducing the size and weight of the transmission and preventing creep.

  Hereinafter, double row ball bearings according to embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
FIG. 1 is a cross-sectional view for explaining a double row ball bearing according to a first embodiment of the present invention. As shown in FIG. 1, the double row ball bearing 1 of this embodiment is provided in the housing 20, and supports the rotating shaft 23 freely.

  The double-row ball bearing 1 includes an inner ring 2 having two rows of raceway grooves on the outer peripheral surface, a pair of outer rings 3 and 3 that are counterbore types each having one row of raceway grooves on the inner peripheral surface, a pair of inner rings 2 and a pair of A plurality of balls 4 arranged in a double row in front combination between both raceway grooves with the outer rings 3 and 3 and a pair of resin cages 5 and 5 that hold the balls 4 in each row at equal intervals in the circumferential direction. And. The double-row ball bearing 1 has a seal 6 fitted to the inner peripheral surface of the outer ring 3, 3 on the counter-bore side.

  The cage 5 includes a large-diameter side annular portion 7 that faces the inner peripheral surface of the outer ring 3 on the counterbore side, and a small-diameter side annular portion 8 that faces the inner peripheral surface on the counter-counter side. An annular projection 9 is provided on the outer peripheral surface of the large-diameter side annular portion 7 so as to protrude in the circumferential direction, and this projection 9 is provided on the counter bore side of the opposing outer ring 3. It engages with a groove 10 provided on the peripheral surface.

  The outer rings 3 and 3 are brought into contact with the end surfaces on the counterbore side of each other, and the opposite counterbore side end surface of one outer ring 3 is brought into contact with the side surface of the flange portion 21 of the housing 20. It is stored. Then, the annular retainer plate 11 is brought into contact with the end surface on the counter-counter side of the other outer ring 3, and the retainer plate 11 is attached to the housing 20 with a plurality of bolts 12 penetrating through the through holes 22 formed in the housing 20. Thus, a preload is applied to the outer rings 3 and 3 and the outer rings 3 and 3 are fixed to the housing 20.

  The inner ring 2 is externally fitted to the rotation shaft 23 and is fixed to the rotation shaft 23 by a retaining ring 13. The fitting between the inner ring 2 and the rotating shaft 23 is a loose fit for improving the assemblability.

  An annular groove 14 is formed on the inner peripheral surface of the inner ring 2 in the axial direction at the intermediate portion in the axial direction. The annular groove 14 has a rubber O-ring, resin, metal, or the like. An annular member 15 made of the above member is attached. The annular member 15 is compressed and inserted into the annular groove 8, and bulges from the annular groove 8 to the outer peripheral surface side of the rotary shaft 23 in a compressed state and presses against the outer peripheral surface of the rotary shaft 23. .

  In the double-row ball bearing 1 of the present embodiment configured as described above, the outer ring is divided into two parts, and the outer rings 3 and 3 are fixed to the housing 20 using the bolts 12 and the backing plate 11, thereby preloading. Is appropriately applied to the outer rings 3 and 3. Accordingly, it is not necessary to apply a preload to the inner ring 2, the inner ring 2 can be fixed by the retaining ring 13, and a large nut such as M20 to M50 for fixing the inner ring 2 in the axial direction is not necessary. Accordingly, a space for arranging a large nut is not necessary, and the degree of freedom in designing the transmission can be improved. Further, by fastening the outer rings 3, 3 to the housing 20 using the bolts 12, the outer rings 3, 3 can be easily detached from the housing 20 compared to the conventional engagement of the outer ring with the retaining ring.

  In addition, the retainer 5 is mounted on the outer ring 3 by engaging the protrusion 9 provided on the outer peripheral surface thereof with the groove 10 provided on the inner peripheral surface of the outer ring 3, so that it can be assembled or disassembled. Sometimes, the outer ring 3 and the cage 5 can be prevented from separating.

  Further, the annular member 15 is compressed and inserted into an annular groove 14 provided on the inner peripheral surface of the inner ring 2, and is pressed against the outer peripheral surface of the rotary shaft 23. A frictional force is generated between them, and the sliding of the mating surface, which is the cause of creep, can be prevented by this frictional force, and the generation of abnormal noise caused by creep wear can be prevented.

(Second Embodiment)
Next, with reference to FIG. 2, the double row ball bearing which concerns on 2nd Embodiment of this invention is demonstrated. In addition, about the part equivalent to 1st Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  FIG. 2 is a cross-sectional view for explaining a double row ball bearing according to a second embodiment of the present invention. In the double-row ball bearing 30 of the present embodiment, notches 32 and 32 are formed at the edges of the outer ring 31 and the outer peripheral surface on the counter-counter side and the end surface on the counter-counter side, respectively. The cutout portion 32 of one outer ring 31 is in contact with the flange portion 21 of the housing 20, and the cutout portion 32 of the other outer ring 31 is in contact with the retainer plate 11. Then, the retainer plate 11 is fixed to the housing 20 by tightening a plurality of bolts 12, so that a preload is applied to the outer rings 31, 31 and the outer rings 31, 31 are fixed to the housing 20.

  Therefore, in the double row ball bearing 30 of the present embodiment, the outer rings 31, 31 are provided with notches 32, 32, and the notches 32, 32 are brought into contact with the flange portion 21 of the housing 20 and the retainer plate 11. The space in the axial direction of the double row ball bearing 30 can be reduced by the space of the notches 32 and 32.

As shown in FIG. 3, when the double row ball bearing 30 of this embodiment is applied to the housing 20 in which the through hole 22 cannot be formed, the retainer plate 11 is tightened with the stud bolt 33. It can be configured according to the design of the transmission.
Other configurations and operations of the present embodiment are the same as those of the first embodiment.

In addition, this invention is not limited to each embodiment mentioned above, A suitable deformation | transformation, improvement, etc. are possible.
In the present embodiment, the total axial width of the outer ring and the inner ring is made equal, but may be different. The pair of outer rings have the same axial width, but may be different. Furthermore, the balls may be arranged symmetrically or asymmetrically.

  In this embodiment, the member for preventing creep of the inner ring is formed in an annular shape, but any shape can be designed as long as it can reliably prevent creep. In addition, the groove in which the prevention member is mounted is also an annular groove in the present embodiment, but can be arbitrarily designed according to the shape of the member that prevents the inner ring from creeping. Moreover, although the groove | channel which accommodates the said prevention member was made into one place, you may make it provide in multiple places on the internal peripheral surface of an inner ring | wheel. Moreover, although the projection part formed in the holder | retainer was made into the annular | circular shape, you may make it protrude in the radial direction in multiple places over the circumferential direction.

  The seal of the present embodiment is of a non-contact type with the inner ring, but may be of a contact type, and the seal can be arbitrarily designed. Furthermore, the structure without a seal | sticker may be sufficient.

It is sectional drawing for demonstrating the double row ball bearing which concerns on 1st Embodiment of this invention. It is sectional drawing for demonstrating the double row ball bearing which concerns on 2nd Embodiment of this invention. It is sectional drawing for demonstrating the double row ball bearing which concerns on the modification of 2nd Embodiment of this invention. It is sectional drawing for demonstrating the conventional back combination type double row ball bearing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,30 Double row ball bearing 2 Inner ring 3,31 Outer ring 4 Ball 5 Resin cage 7 Large-diameter side annular part 8 Small-diameter side annular part 9 Projection part 10 Groove part 11 Retainer plate 12 Bolt 13 Retaining ring 14 Annular groove 15 Annular member 20 Housing 23 Rotating shaft 32 Notch

Claims (4)

An inner ring having two rows of raceway grooves on the outer peripheral surface, a pair of outer rings each having a row of raceway grooves on the inner peripheral surface, and a double row in front combination between both raceway grooves of the inner ring and the pair of outer rings A plurality of balls arranged in a pair, and a pair of resin cages holding the balls in each row at equal intervals in the circumferential direction;
With
The retainer is attached to the outer ring by engaging a protrusion provided on the outer peripheral surface thereof with a groove provided on the inner peripheral surface of the outer ring,
A double row ball bearing, wherein a groove is formed on an inner peripheral surface of the inner ring, and a member for preventing creep of the inner ring is attached to the groove. Each of the outer rings is a counterbore type,
The cage includes a large-diameter side annular portion facing the inner peripheral surface of the outer ring on the counterbore side, and a small-diameter side annular portion facing the inner peripheral surface on the counter-counter side,
2. The compound according to claim 1, wherein the projecting portion is formed on an outer peripheral surface of the large-diameter side annular portion, and the groove portion is provided on an inner peripheral surface of the outer ring on the counter bore side. Row ball bearing.   The double row ball bearing according to claim 1, wherein the member is one of an O-ring, a resin member, and a metal member.   The double row ball bearing according to any one of claims 1 to 3, wherein the outer ring includes a notch on an outer peripheral surface on the counter-bore side.

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