JP2009008179A - Outer ring for rocking bearing, rocking bearing and air disk brake device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an outer ring for a rocking bearing capable of being closely contacted with a housing at appropriate preload. <P>SOLUTION: The outer ring 12 for the rocking bearing is provided with an arcuate raceway member 13 having a raceway surface on the inner diameter face and with flange parts 14 provided in axial both end parts of the raceway member 13 to be protruded to the radial inner side. When the circumferential length of the raceway member 13 is defined as L<SB>1</SB>and the circumferential length of the flange part 14 as L<SB>2</SB>, 0.2≤ L<SB>2</SB>/L<SB>1</SB>≤0.8 is satisfied. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a rocking bearing outer ring, a rocking bearing, and an air disc brake device.

A conventional rocking bearing is described in, for example, WO2006 / 002905A1 (Patent Document 1). An oscillating bearing described in the publication includes an arc-shaped oscillating bearing outer ring having a raceway surface on an inner diameter surface, a plurality of rollers disposed along the raceway surface, and a cage that holds the plurality of rollers. With. In addition, in order to restrict the movement of the rollers and the cage in the width direction, flanges that protrude radially inward from both ends in the width direction are formed over the entire circumferential direction of the outer ring for the rocking bearing.
WO2006 / 002905A1

  When the swing bearing having the above configuration is incorporated in the housing, if there is a gap between the outer ring for swing bearing and the housing, there is a risk of rattling or the like during swinging. Therefore, there is known a method in which the radius of curvature of the outer ring for rocking bearing is set larger than the radius of curvature of the housing in advance, and a force (hereinafter referred to as “preload”) is applied in a direction to reduce the radius of curvature of the outer ring for rocking bearing. It has been.

  However, the provision of the flange improves the rigidity against the preload of the rocking bearing outer ring. That is, as compared with a rocking bearing outer ring having no flange, it cannot be incorporated by the above method unless a larger preload is applied. On the other hand, as the preload increases, the rotational torque during swinging also increases. This causes abnormal heat generation of the rocking bearing, and as a result, the life of the rocking bearing is reduced.

  Accordingly, an object of the present invention is to provide an outer ring for a rocking bearing that can be brought into close contact with a housing with an appropriate preload. It is another object of the present invention to provide a rocking bearing and an air disc brake device having a long life and high reliability by employing such a rocking bearing outer ring.

An outer ring for a rocking bearing according to the present invention includes an arc-shaped race member having a raceway surface on an inner diameter surface, and flanges projecting radially inward at both end portions in the width direction of the race member. When the circumferential length of the raceway member is L ₁ and the circumferential length of the collar portion is L ₂ , 0.2 ≦ L ₂ / L ₁ ≦ 0.8 is satisfied. Here, if the value of L ₂ / L ₁ is 0.8 or less, the rigidity of the outer ring for rocking bearing can be sufficiently reduced. On the other hand, if the value of L ₂ / L ₁ is made smaller than 0.2, the movement of the cage in the width direction cannot be properly regulated. As a result, the inclination of the cage with respect to the circumferential direction of the rocking bearing is increased, and the behavior of the cage and the rollers becomes unstable. Therefore, by limiting the circumferential length of the flange within the above range, the outer ring for the rocking bearing can be brought into close contact with the housing with an appropriate preload, and the movement of the cage in the width direction is appropriately restricted. can do.

  A rocking bearing according to the present invention includes the rocking bearing outer ring described above, a plurality of rollers disposed along the raceway surface, and a cage that holds the plurality of rollers. Thereby, a long-life and highly reliable rocking bearing can be obtained.

  Preferably, the flange portion further includes a projecting portion that extends inward in the width direction from the tip thereof and holds the retainer from the radially inner side. More preferably, the cage has a ridge that is continuous in the circumferential direction on an end surface facing the flange. And a protrusion part hold | maintains a protrusion from radial inside. Thereby, it is possible to effectively prevent the retainer from coming off in the radial direction of the rocking bearing outer ring.

  Preferably, the collar portion is located in a central region in the circumferential direction of the track member. Thereby, a holder | retainer can be inserted along a track surface from the circumferential direction edge part of a track member. As a result, the assemblability of the rocking bearing is improved.

  An air disc brake device according to the present invention includes any one of the rocking bearings described above. Thereby, a long life and highly reliable air disc brake can be obtained.

  According to this invention, the rigidity of the outer ring for the rocking bearing is reduced by providing the flange portion limited to only a part of the raceway member in the circumferential direction, so that the rocking can be brought into close contact with the housing with an appropriate preload. An outer ring for a dynamic bearing can be obtained. In addition, by adopting such an outer ring for a rocking bearing, it is possible to obtain a rocking bearing and an air disc brake device having a long life and high reliability.

  A rocking bearing 11 according to an embodiment of the present invention will be described with reference to FIGS. 1 is a view as seen from the direction of the arrow I in FIG. 3, FIG. 2 is a perspective view of the rocking bearing 11, FIG. 3 is a perspective view of the rocking bearing outer ring 12, and FIG. FIG. 5 is a cross-sectional view taken along line V-V in FIG. 2.

  First, referring to FIG. 2, rocking bearing 11 holds rocking bearing outer ring 12, a plurality of rollers 15 disposed along the inner diameter surface of rocking bearing outer ring 12, and a plurality of rollers 15. And a retainer 16.

  Next, referring to FIG. 3, the rocking bearing outer ring 12 includes a raceway member 13 having a circular arc shape (in this embodiment, a semicircular shape with a central angle of 180 °) having a raceway surface 13a on the inner diameter surface, and a raceway. It includes a flange 14 that protrudes radially inward from both widthwise ends of the member 13 and restricts movement of the rollers 15 and the cage 16 in the width direction.

  The track member 13 has outward protruding pieces 13b at both ends in the circumferential direction, an inward protruding piece 13c at one circumferential end (left side in FIG. 2), and the other circumferential end ( A claw portion 13d is provided on the right side in FIG. The flange portion 14 is provided with a protruding portion 14 a extending from the tip thereof toward the inner side in the width direction of the track member 13.

  The outward projecting piece 13b extends radially outward from the center in the width direction of both end surfaces of the raceway member 13 in the circumferential direction. The outward projecting piece 13b engages with a housing (not shown) to prevent the rocking bearing outer ring 12 from moving in the circumferential direction, that is, the rocking bearing outer ring 12 from rotating inside the housing. .

  The inward protruding pieces 13c extend radially inward from two places on both sides in the width direction of the outward protruding pieces 13b. The inwardly projecting piece 13c abuts on the circumferential end surface of the retainer 16 to prevent the retainer 16 from coming off to one side in the circumferential direction.

  The claw portion 13 d extends from the end surface in the width direction of the race member 13 toward the inside in the radial direction. The claw portion 13 d is located on the inner side in the width direction of the track member 13 than the collar portion 14. The claw portion 13d engages with the protrusion 16d of the retainer 16 to prevent the retainer 16 from coming off to the other circumferential side.

Next, referring to FIG. 1, the flange portion 14 is formed only on a part of the raceway member 13 in the circumferential direction. Specifically, the track member 13 is located in a central region in the circumferential direction (refers to “a region including the swing center of the swing bearing 11”). Then, when the circumferential length of the race member 13 is L ₁ and the circumferential length of the flange 14 is L ₂ , the flange portion satisfies 0.2 ≦ L ₂ / L ₁ ≦ 0.8. 14 to set the circumferential length _{L 2} of the.

Here, if L ₂ / L ₁ ≦ 0.8, the rigidity of the rocking bearing outer ring 12 can be sufficiently reduced. On the other hand, if L ₂ / L ₁ <0.2, the rigidity of the flange portion 14 becomes too low, and the movement of the cage 16 in the width direction cannot be appropriately restricted. As a result, the inclination of the cage 16 with respect to the circumferential direction of the rocking bearing 11 becomes large, and the behavior of the rollers 15 and the cage 16 becomes unstable.

  Therefore, by forming the flange portion 14 limited to a part in the circumferential direction of the track member 13 as in the above configuration, the outer ring 12 for rocking bearing can be brought into close contact with the housing with an appropriate preload. The movement of the cage 16 in the width direction can be appropriately restricted.

In FIG. 1, the outward projecting piece 13b, the inward projecting piece 13c, and the claw portion 13d are not shown. Further, the claw portions 13d are different roles from the flange portion 14, the circumferential length L ₂ of the flange portion 14, and does not include the claw portion 13d.

  The rocking bearing outer ring 12 having the above configuration is manufactured by, for example, pressing a steel plate. Specifically, first, a substantially rectangular flat plate is obtained from a steel plate by punching. Next, the track member 13 and the flange portion 14 are formed by bending. Specifically, the track member 13 can be formed by curving the longitudinal direction of the flat plate to a predetermined curvature. Further, the flange portion 14 can be formed by bending both ends of the flat plate in the short direction at right angles to the track member 13.

  In the formation process of the race member 13, the bending process is performed a plurality of times, and gradually approaches a predetermined curvature. Similarly, in the step of forming the flange portion 14, bending is performed a plurality of times and bent little by little. In addition, it is desirable that the bending process for forming the race member 13 and the bending process for forming the flange portion 14 are alternately performed so as to gradually approximate the shape of the rocking bearing outer ring 12. At this time, since the flange portion 14 is formed so as to be limited to a part of the circumferential direction of the race member 13, the race member 13 and the flange portion 14 are compared with the case where the flange portion is provided in the entire circumferential direction of the race member. Can be easily formed.

  Further, the protruding portion 14 a is formed by bending the tip of the flange portion 14 toward the inner side in the width direction of the track member 13. Further, the outward projecting piece 13b, the inward projecting piece 13c, and the claw portion 13d are formed by bending.

  Next, heat treatment is applied to the outer ring 12 for rocking bearing in order to impart predetermined mechanical properties. Specifically, carbonitriding or carburizing and quenching is performed. Thereby, the surface is hard, the inside is soft, and the property with high toughness is obtained. Further, in order to reduce the residual stress and internal strain generated by the heat treatment and to improve the toughness and stabilize the dimensions, it is desirable to perform tempering after the heat treatment.

  Next, in order to make the surface roughness of the inner diameter surface of the raceway member 13 which becomes the raceway surface 13a equal to or less than a predetermined value, barrel polishing is applied to the outer ring 12 for rocking bearing. By setting the surface roughness of the raceway surface 13a to a predetermined value or less, the frictional resistance between the raceway surface 13a and 15 can be reduced, and torque loss and heat generation during swinging can be suppressed. As a result, the rocking bearing 11 having a long life and high reliability can be obtained.

  Next, referring to FIG. 4, the retainer 16 has a plurality of columnar portions 16 a arranged at predetermined intervals in the circumferential direction, and arc-shaped shapes arranged at both longitudinal ends of the columnar portions 16 a. A pocket 16c that includes the pair of connecting portions 16b and that accommodates the rollers 15 is formed between adjacent column portions 16a. Further, a protrusion 16d that is continuous in the circumferential direction is formed on the end surface of the connecting portion 16b in the width direction (referring to a wall surface facing the flange portion 14 when incorporated in the rocking bearing outer ring 12). ing.

  Further, blank regions 16e in which pockets 16c are not formed are provided at both ends in the circumferential direction of the cage 16. The blank area 16e on one side in the circumferential direction (left side in FIG. 2) is a rotation failure of the roller 15 due to the deformation of the pocket 16c when the circumferential end surface of the cage 16 collides with the inward protruding piece 13c. To prevent. On the other hand, the blank area 16e on the other side in the circumferential direction (right side in FIG. 2) is a portion that protrudes from the outer ring 12 for the oscillating bearing when the cage 16 is maximally biased toward the other side in the circumferential direction. Can not be placed.

  A method for assembling the rocking bearing 11 having the above configuration will be described. First, the roller 15 is assembled in the pocket 16 c of the cage 16. Then, the cage 16 is inserted along the raceway surface 13a from the circumferential end region of the rocking bearing outer ring 12 in which the flange portion 14 is not formed.

  Next, referring to FIG. 5, the protrusion 14 a provided at the tip of the flange 14 holds the protrusion 16 d of the retainer 16 from the inside in the radial direction, and the retainer 16 is supported by the outer ring 12 for the rocking bearing. This prevents it from coming off in the radial direction.

  In addition, the wall surface facing the flange portion 14 of the protrusion 16d includes an inclined surface 16f that is inclined in a direction in which the amount of protrusion decreases toward the radially outer side. Further, an inclined surface 14b is provided at the tip of the protruding portion 14a so as to be inclined in the direction of decreasing the protruding length of the protruding portion 14a toward the radially inner side. These inclined surfaces 14b and 16f function as insertion guide surfaces when the cage 16 is assembled from the radial direction of the rocking bearing outer ring 12. Thus, if the cage 16 can be incorporated from the radial direction of the rocking bearing outer ring 12, the assemblability of the rocking bearing 11 is further improved.

  In the above embodiment, the protrusion 16a holds the protrusion 16d from the radially inner side. However, the present invention is not limited to this, and the protrusion 16a may directly hold the connecting portion 16b. Good. In this case, the protrusion 16d can be omitted.

  However, when the connecting portion 16 b is directly held by the protruding portion 14 a, the protruding length of the flange portion 14 must be longer than the thickness dimension of the cage 16. On the other hand, when holding the protrusion 16d by the protrusion 14a, the protrusion length of the flange 14 may be longer than the thickness dimension of the protrusion 16d. In other words, as shown in FIG. 5, the protrusion length of the flange portion 14 can be shortened if the protrusion 16 d is provided so as to be biased outward in the radial direction of the cage 16. Therefore, from the viewpoint of shortening the protruding length of the flange portion 16, it is desirable to provide a protrusion 16 d on the end surface in the width direction of the cage 16 and engage the protrusion 14 a and the protrusion 16 d.

  Further, the outward projecting piece 13b, the inward projecting piece 13c, and the claw portion 13d are not essential components of the present invention and can be omitted. Moreover, although the nail | claw part 13d in said embodiment showed the example engaged with the protrusion 16d of the holder | retainer 16, it is not restricted to this, The nail | claw part 13d is engaged with the end surface of the holder | retainer 16 in the width direction. Protruding protrusions may be provided separately.

  In the above embodiment, the example in which the inwardly projecting piece 13c is provided at one end in the circumferential direction of the track member 13 and the claw portion 13d is provided at the other end in the circumferential direction is shown. However, the inwardly protruding pieces 13c may be provided at both ends in the circumferential direction of the track member 13 by omitting the claw portions 13d, and conversely, the inwardly protruding pieces 13c may be omitted and the track member 13 may be omitted. You may provide the nail | claw part 13d in the circumferential direction both ends.

  Furthermore, in the above-described embodiment, the example in which the collar portion 14 is arranged in the central region in the circumferential direction of the raceway member 13 has been described. However, the present invention is not limited to this, and any number can be provided at any position. . A rocking bearing outer ring 22 according to another embodiment of the present invention will be described with reference to FIG. FIG. 6 is a view corresponding to FIG. 1 of the outer ring 22 for rocking bearing. In addition, description of a common point with the rocking | fluctuation bearing outer ring | wheel 12 shown in FIG. 1 and FIG. 3 is abbreviate | omitted, and it demonstrates centering around difference.

  Referring to FIG. 6, rocking bearing outer ring 22 includes a race member 23 and flanges 24 a and 24 b (collectively referred to as “hook 24”). The flange 24a is an end region on one side in the circumferential direction of the track member 23 (left side in FIG. 6), and the flange 24b is an end region on the other side in the circumferential direction of the track member 23 (right side in FIG. 6). Respectively.

Thus, the flange portion 24a, even in the case where the 24b at an arbitrary position, the circumferential length _{L 1} of the raceway member 23, circumferential flange portion 24 the length _{L 2} and is 0.2 ≦ L The effect of the present invention can be obtained as long as ₂ / L ₁ ≦ 0.8 is satisfied. Incidentally, the circumferential length L ₂ of the flange portion 24 in this case corresponds to the sum of the circumferential length L ₄ of the circumferential length L ₃ and the flange portion 24b of the flange portion 24a.

  Next, an air disc brake device 71 according to an embodiment of the present invention will be described with reference to FIGS. 7 is a schematic sectional view of the air disk brake device 71, and FIG. 8 is an enlarged sectional view of the braking mechanism 80.

  First, referring to FIG. 7, an air disc brake device 71 includes a brake disc 72 (also referred to as “rotor”) that rotates integrally with a tire (not shown), a pair of brake pads 73 and 74, and a brake cylinder 75. The brake mechanism 80 is mainly provided.

  The pair of brake pads 73 and 74 are disposed at positions adjacent to the brake disk 72 in the axial direction. In addition, a predetermined gap is provided between the brake disc and the brake pads 73 and 74 in a non-braking state (referring to a state where the brake pedal is not depressed).

  The brake cylinder 75 includes an air chamber 76 having a variable volume, an intake / exhaust port 77 that supplies and discharges air to / from the air chamber 76, and an axial direction (“in FIG. An actuator rod 78 that moves in the direction of arrow A and the opposite direction thereof, and a coil spring 79 as an elastic member that urges the actuator rod 78 in a direction that reduces the volume of the air chamber 76.

  The brake mechanism 80 has a swing member 81 at one end, is connected to the actuator rod 78 at the other end, and rotates around a swing center G of the swing member 81. The swinging bearing 11 according to an embodiment of the present invention that swingably supports the swinging member 81 is attached to a position deviated from the swinging center G of the swinging member 81 and axially (see FIG. 7). And a coil spring 84 as an elastic member that urges the traverse 83 in a direction away from the brake pads 73 and 74.

  The air disk brake device 71 having the above-described configuration is employed in, for example, a large vehicle requiring a large braking force, such as a large commercial vehicle, a truck, or a bus.

  The operation of the air disc brake device 71 configured as described above will be described. First, when a brake pedal (not shown) is depressed, air is supplied from the intake / exhaust port 77 to the air chamber 76, and the volume of the air chamber 76 increases. As the volume of the air chamber 76 increases, the actuator rod 78 moves in the direction of arrow A against the elastic force of the coil spring 79. The turning lever 82 pushed by the actuator rod 78 turns counterclockwise around the swing center G (the position of the turning lever 82 after turning is indicated by a one-dot chain line in FIG. 8). A traverse 83 attached at a position off the swing center G of the swing member 81 moves in the direction of arrow B against the elastic force of the coil spring 84. As a result, the brake pads 73 and 74 are pressed against the brake disc 72, and the rotation of the tire is braked.

  On the other hand, when the brake pedal is loosened, the air in the air chamber 76 is discharged from the intake / exhaust port 77, and the volume of the air chamber 76 decreases. As the volume of the air chamber 76 decreases, the coil spring 79 moves the actuator rod 78 in the direction opposite to the arrow A. The rotation lever 82 connected to the actuator rod 78 rotates clockwise around the swing center G. The coil spring 84 moves the traverse 83 in the direction opposite to the arrow B. As a result, a predetermined gap is formed between the brake disc 72 and the brake pads 73 and 74, and the braking of the tire is released.

  In the air disc brake device 71 configured as described above, the rocking bearing 11 according to one embodiment of the present invention is employed as a bearing that rockably supports the rocking member 81, thereby providing a long-life and highly reliable air. A disc brake device 71 can be obtained.

  As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

  The present invention is advantageously used for a rocking bearing.

FIG. 4 is an arrow view seen from the direction of arrow I in FIG. 3. 1 is a perspective view of a rocking bearing according to an embodiment of the present invention. It is a perspective view of the outer ring | wheel for rocking | fluctuation bearings shown in FIG. It is a perspective view of the holder | retainer shown in FIG. It is sectional drawing in VV of FIG. It is a figure which shows other embodiment of FIG. It is a figure showing an air disc brake device concerning one embodiment of this invention. It is the elements on larger scale of FIG.

Explanation of symbols

  11 Oscillating bearing, 12, 22 Oscillating bearing outer ring, 13, 23 race member, 13a raceway surface, 13b outward projecting piece, 13c inward projecting piece, 13d claw part, 14, 24, 24a, 24b collar part, 14a Protruding part, 15 rollers, 16 cage, 16a pillar part, 16b connecting part, 16c pocket, 16d ridge, 16e blank area, 14b, 16f inclined surface, 71 air disk brake device, 72 brake disk, 73, 74 brake Pad, 75 Brake cylinder, 76 Air chamber, 77 Air intake / exhaust port, 78 Actuator rod, 79, 84 Coil spring, 80 Braking mechanism, 81 Oscillating member, 82 Rotating lever, 83 Traverse

Claims (6)

An arc-shaped raceway member having a raceway surface on the inner diameter surface;
It comprises a flange projecting radially inward at both ends in the width direction of the track member,
When the circumferential length of the track member is L ₁ and the circumferential length of the flange is L ₂ ,
An outer ring for a rocking bearing that satisfies 0.2 ≦ L ₂ / L ₁ ≦ 0.8. An outer ring for a rocking bearing according to claim 1,
A plurality of rollers disposed along the raceway surface;
A rocking bearing comprising a cage for holding the plurality of rollers.   The rocking bearing according to claim 2, wherein the flange portion further includes a projecting portion that extends inward in the width direction from the tip thereof and holds the retainer from the radially inner side. The retainer has a ridge that is continuous in the circumferential direction on an end surface facing the flange,
The rocking bearing according to claim 3, wherein the protrusion holds the protrusion from the radially inner side.   The rocking bearing according to any one of claims 2 to 4, wherein the flange is located in a central region of the raceway member in a circumferential direction.   An air disc brake device comprising the rocking bearing according to claim 2.

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