JP2009030631A - Sealing device and rolling bearing device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a sealing device enabling the remarkable reduction of torque and not loosened off. <P>SOLUTION: An elastic member 51 comprises a base 53 secured to a core member 50, first and second axial lips 54, 55 sliding on the flange part 66 of a slinger 52, and an annular projection part 56 projecting from the base 53. When the sealing device is used in nonabrasive state, the elastic member 51 is positioned at an interval from the slinger 52. When the sealing device is not in use during the transportation or the like, a predetermined axial force is added between the slinger 52 and a seal member 48 to bring the projection part 56 into contact with the fixed part 65 of the slinger 52 while the projection part 56 is bent to the flange 66 side of the slinger in the axial direction and substantially held stationary on the fixed part 65 of the slinger 52. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a sealing device. The present invention also relates to a rolling bearing device having a sealing device.

  Conventionally, as a sealing device, there is one described in Japanese Utility Model Publication No. 4-93571 (Patent Document 1).

  This sealing device is disposed between the inner race and the outer race of the hub unit. The sealing device includes a metal core member, an elastic member fixed to the metal core member, a slinger having an L-shaped cross section, and a garter spring. The slinger includes an axially extending portion and a radially extending portion, and the elastic member slides on the radial lip that always slides on the axially extending portion and on the radially extending portion. A first axial lip; and a second axial lip that is positioned radially inward of the first axial lip and slides on the radially extending portion. The second axial lip has an annular groove on the outer surface in the radial direction.

  The garter spring is fitted into the annular groove of the second axial lip. The garter spring plays a role of pressing the second axial lip inward in the radial direction.

In such a background, in the hub unit, it is desired to significantly reduce the torque of the sealing device that seals the rolling elements to the outside. Conventionally, when the sealing device is transported or when the sealing device is assembled, the slinger, the elastic member, and the metal core member may be separated, and the sealing device may be scattered. For this reason, it is desired to prevent the sealing device from being scattered when the sealing device is transported or when the sealing device is assembled.
Japanese Utility Model Publication No. 4-93571 (FIG. 1)

  SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a sealing device that can significantly reduce torque and that does not generate any fluctuations.

In order to solve the above problems, the sealing device of the present invention is:
Seal member having a cylindrical fixing part, a cored bar member having a radially extending part extending from the fixing part in a substantially radial direction of the fixing part, and an elastic member fixed to the cored bar member When,
A slinger having a cylindrical fixing portion and a flange portion extending substantially in the radial direction from the fixing portion;
The elastic member is
A base fixed to the radially extending portion of the core member;
A first axial lip extending from the base and sliding on the flange;
Non-wearing state during use after assembly after the seal member is incorporated in the slinger while being positioned between the first axial lip and the fixed portion of the slinger and sliding on the flange portion A second axial lip located at a distance from the fixed portion of the slinger;
It consists of an annular protrusion that protrudes from the base,
The protrusion has a portion that is positioned at an interval from the slinger in the non-wearing state at the time of use and overlaps the fixed portion of the slinger in the axial direction.
The seal member and the slinger have an axial interval that is shorter than an axial interval between the radially extending portion and the flange portion during the use in a state before use before the use. Arranged so that
The protruding portion is in contact with the fixing portion of the slinger in a state in which the protruding portion is bent toward the flange portion of the slinger in the axial direction and is substantially stationary with respect to the fixing portion of the slinger in the pre-use state. It is characterized by becoming.

  The non-wearing state at the time of use is assumed when the lip is in a non-wearing state and the axial preload between the slinger and the seal member is assumed at the start of use of the sealing device when the lip is in the non-wearing state. It means a state that is within the preload range.

  Moreover, the said state before use means the state before integrating a slinger and a sealing member in a sealing object.

  The inventor is a so-called pack-sealing type sealing device having a cored bar member, an elastic member, and a slinger having an L-shaped cross section, which has two radial lips and one axial lip. The magnitude of the torque caused by the lip contact load was investigated. As a result, the ratio of the torque due to the contact load of the two radial lips reached about 80%, and it was found that most of the torque was due to the contact load of the radial seal.

  According to the present invention, the second axial lip is positioned in the radial direction with respect to the fixed portion of the slinger in a non-wearing state during use after the elastic member is incorporated into the slinger. In addition, since the projecting portion is located at a distance from the slinger fixing portion and there is no radial lip in contact with the slinger fixing portion, in the non-wearing state, the torque Can be drastically reduced, and fuel consumption of an automobile or the like having this sealing device can be reduced.

  Further, in the present invention, compared to the configuration in which a radial contact lip is present, in the initial state of non-wear, there is no radial contact lip, so the torque can be significantly reduced, while the radial contact lip This eliminates the frictional force in the axial direction due to the absence of the elastic member, and the elastic member and the metal core member easily move in the axial direction with respect to the slinger when the sealing device is transported or when the sealing device is assembled. There is a fear.

  However, according to the present invention, the seal member and the slinger have an axial interval that is shorter than the axial interval between the radially extending portion and the flange portion during the use in a state before use. In this pre-use state, the projecting portion comes into contact with the fixed portion of the slinger in a substantially stationary state. For example, a machine such as a hub unit incorporating the sealing device In a pre-use state such as when the sealing device is transported before being assembled into the device, the protruding portion can be brought into contact with the fixed portion of the slinger in a substantially stationary state. Therefore, it is possible to prevent the seal member from being separated from the slinger in the state before use.

  Further, according to the present invention, the protrusion has a portion that is positioned at an interval from the slinger in the non-wearing state at the time of use and overlaps the fixing portion of the slinger in the axial direction. In the non-wearing state, the protruding portion and the fixed portion of the slinger constitute a labyrinth seal. Therefore, the sealing performance can be improved in the non-wearing state.

  Further, according to the present invention, the seal member and the slinger have an axial interval shorter than an axial interval between the radially extending portion and the flange portion during use in the state before use. In this pre-use state, the projecting portion is bent toward the flange portion of the slinger in the axial direction and is substantially stationary on the fixing portion of the slinger. Since it comes into contact with the fixed portion, in this state, the protruding portion receives force from the fixed portion of the slinger to the flange portion side, that is, the anti-scattering side. Therefore, it is possible to increase the dispersal deterrence force when not in use.

  Further, when the sealing member and the slinger are incorporated into a sealed object, the pre-use state in a non-wearing state during use from a short axial interval between the radially extending portion and the flange portion in the pre-use state The interval is longer than the axial interval. At this time, it can suppress that the said protrusion part reverses and the said sealing member and the said slinger do not move to an axial direction.

The rolling bearing device of the present invention is
A first race member having a raceway surface;
A second race member having a raceway surface;
A plurality of rolling elements disposed between the raceway surface of the first raceway member and the raceway surface of the second raceway member;
The sealing device according to claim 1, further comprising: an opening on one side in the axial direction between the first track member and the second track member.

  According to the present invention, since the sealing device of the present invention is provided, the torque of the sealing device can be reduced during operation, and the fuel consumption of the machine having the rolling bearing device of the present invention can be reduced.

In one embodiment of the sealing device,
The second axial lip is connected to the first portion extending from the base in a direction approaching the fixing portion of the slinger, and is connected to the first portion via a bent portion, and is connected to the fixing portion of the slinger. A second portion that extends in a direction away from the second portion and slides on the flange portion;
In a state after the elastic member is incorporated in the slinger, and in a state where the pressing force of the second axial lip against the flange portion is reduced by a predetermined force or more due to wear of the second axial lip, the bent portion is , And slides on the fixed part of the slinger.

  According to the above-described embodiment, the bending portion comes into contact with the fixing portion of the slinger in a state where the pressing force against the flange portion of the second axial lip is reduced by a predetermined force or more due to wear of the second portion of the second axial lip. In addition, even if the wear of the second axial lip is accelerated, foreign matter such as muddy water from the outside is placed on the rolling elements of the hub unit even if the second axial lip wears. Intrusion into the space can be suppressed.

In one embodiment of the sealing device,
In a state before the elastic member is incorporated in the slinger, the radially inner surface of the first portion is a concave surface, while the radially inner surface of the second portion is a cone. It is a surface or a convex surface.

  In this specification, the conical surface is included in the concave surface, but not included in the convex surface.

  In the sealing device having the conventional configuration, the inventor has a large deformation of the radially inner axial lip portion on the core metal member side, and stress concentration occurs in this portion. As a result, the lifetime of the sealing device was shortened.

  According to the embodiment, the radially inner surface of the first portion is a concave surface in a state before assembly before the elastic member is incorporated into the slinger. Unlike the case where the inner surface of the first axial lip is convex, in the initial state of the built-in state, the second axial lip is not in contact with the fixed portion of the slinger. It is not necessary to intensively and excessively deform a part on the base side, and by deforming the entire first part substantially evenly in its extending direction, the second axial lip can be moved with respect to the fixing part of the slinger. Can be contactless. Therefore, local and excessive stress is not applied to a part of the first portion, so that the durability of the second axial lip can be remarkably improved and the life of the sealing device can be extended.

  Further, according to the above embodiment, the radially inner surface of the second portion is a conical surface or a convex surface in the state before the assembly, and thus the radially inner surface of the second portion. Compared with the case where the surface of the second axial lip is concave, the contact surface pressure between the second axial lip and the flange portion of the slinger can be reduced, and wear of the second axial lip can be suppressed. Therefore, since the time until the second axial lip contacts the fixing portion of the slinger can be lengthened, compared to the case where the radially inner surface of the second portion is a concave surface, A state in which the torque is remarkably small can be maintained for a long time.

In one embodiment of the sealing device,
The radially inner surface of the second portion is smoothly connected.

  The term “smoothly connected” means that the radially inner surface of the second portion is in a state that can be differentiated from one end to the other end in the axial section of the sealing device.

  According to the embodiment, since the inner surface in the radial direction of the second portion is smoothly connected, the stress generated due to the deformation of the second axial lip at the time of assembly is applied to the entire second portion. Can be distributed almost evenly. Further, the second axial lip can be easily deformed radially outward at the time of assembly, and the second axial lip can be used in a non-wearing state during use after the first and second axial lips are assembled. And a predetermined clearance can be easily and accurately generated between the slinger and the fixed portion of the slinger.

In one embodiment of the sealing device,
In the state before the assembly, in the axial section, the curvature of the radially inner surface of the first portion increases as it goes outward in the axial direction.

  The phrase “increasing in the axial direction outwards” includes that in the axial cross section, the radially inner surface of the first portion goes outward in the axial direction. In addition, a case where a portion where the curvature is partially constant is included is also included. For this reason, for example, in the above wording, in the axial cross section, the radially inner surface of the first portion is smoothly connected to the conical surface located on the base side and the conical surface, and the spheroid The case where it consists of the concave surface which consists of a surface etc. is included.

  According to the embodiment, in the state before the assembly, in the axial section, the curvature of the inner surface in the radial direction of the first portion increases as it goes outward in the axial direction. As a result, the stress caused by the deformation of the second axial lip during assembly can be distributed evenly over the entire first portion, and the non-contact state with respect to the fixed portion of the second axial lip. When this is realized, it is possible to reliably prevent local stress concentration from occurring in the first portion.

  According to the sealing device of the present invention, the elastic member is in a non-contact state with the fixing portion of the slinger in a non-wearing state after use after the elastic member is incorporated into the slinger, There is no lip. Therefore, in the non-wearing state, the torque can be drastically reduced, and the fuel consumption of an automobile or the like having this sealing device can be reduced.

  Further, according to the sealing device of the present invention, the projecting portion applies a predetermined pressure between the slinger and the seal member so that the projecting portion comes into contact with the fixed portion of the slinger in a substantially stationary state. Therefore, for example, in a state before use such as during transportation, the protruding portion can be brought into contact with the fixed portion of the slinger in a substantially stationary state, and in the state before use, It is possible to prevent the sealing member from coming off from the slinger.

  Further, according to the sealing device of the present invention, the protruding portion has a portion that is positioned at an interval from the slinger and overlaps the fixed portion of the slinger in the non-wearing state during use. In the non-wearing state, the protruding portion and the fixed portion of the slinger constitute a labyrinth seal, so that the sealing performance can be improved in the non-wearing state.

  Further, according to the sealing device of the present invention, the seal member and the slinger are shafts that are shorter than an axial interval between the radially extending portion and the flange portion during use in a state before use. In this pre-use state, the protruding portion is bent toward the flange portion side of the slinger in the axial direction and substantially stationary to the fixing portion of the slinger. In this state, the projecting portion receives a force from the slinger fixing portion to the flange portion side, and in the state before use such as during transportation, It can increase the deterrence. Further, when the sealing member and the slinger are incorporated into a sealed object, the pre-use state in a non-wearing state during use from a short axial interval between the radially extending portion and the flange portion in the pre-use state The interval is longer than the axial interval. At this time, it can suppress that the said protrusion part reverses and the said sealing member and the said slinger do not move to an axial direction.

  Hereinafter, the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a sectional view in the axial direction of a hub unit which is an embodiment of the rolling bearing device of the present invention.

  The hub unit includes an inner shaft 2 as a first track member, an outer ring 3 as a second track member, an inner ring 4 as a first track member, a plurality of first balls 5 as a plurality of rolling elements, a plurality of rolling elements. A plurality of second balls 6 as moving bodies, a first sealing device 8 according to an embodiment of the present invention, and a second sealing device 9 according to an embodiment of the present invention are provided.

  The inner shaft 2 has a disc-shaped brake disk mounting flange 10 extending in the radial direction to which the brake disk 11 is mounted at one end in the axial direction. A plurality of bolt through holes are formed on a concentric circle centered on the approximate center of the brake disk mounting flange 10. With the brake disc 11 in contact with the brake disc mounting flange 10 and further with the wheel member 13 in contact with the brake disc 11, the end surface of the wheel member 13 opposite to the brake disc 11 side, The disk mounting flange 10 is fixed with a plurality of bolts 15.

  An inner ring 4 is externally fitted and fixed to the other axial end of the inner shaft 2. In the axial direction, an angular first raceway groove 16 is formed between the inner ring 4 and the brake disk mounting flange 10 in the inner shaft 2, while the outer circumferential surface of the inner ring 4 is angular. A second track groove 17 of the mold is formed.

  The outer ring 3 is arranged on the other end side of the brake disc mounting flange 10 in the inner shaft 2 so as to face the inner shaft 2 in the radial direction. The outer ring 3 has a vehicle body side mounting flange 14 that extends in the radial direction on the other end side in the axial direction. A plurality of bolt through holes for inserting bolts for attaching the vehicle body side mounting flange 14 to the vehicle body side (knuckle) are formed in the disk-shaped vehicle body side mounting flange 14. The outer ring 3 has an angular third track groove 26 and a fourth track groove 27 that are axially spaced from each other on the inner peripheral surface of the outer ring 3, and the angular third track groove 26 is an angular type. It is located on the one end side with respect to the fourth track groove 27.

  The first ball 5 is spaced apart from the first raceway groove 16 of the inner shaft 2 and the third raceway groove 26 of the outer ring 3 by a predetermined distance in the circumferential direction while being held by the cage 18. Are arranged. The second ball 6 is held at a predetermined interval in the circumferential direction while being held by the cage 19 between the second raceway groove 17 of the inner ring 4 and the fourth raceway groove 27 of the outer ring 3. Several are arranged.

  The first sealing device 8 is disposed in the vicinity of the opening on the one end side (the brake disc mounting flange 10 side) in the axial direction between the inner shaft 2 and the outer ring 3. The first sealing device 8 seals the opening on the one end side of the space between the inner shaft 2 and the outer ring 3. On the other hand, the second sealing device 9 is disposed between the inner ring 4 and the outer ring 3 in the vicinity of the opening on the other end side in the axial direction (the side opposite to the brake disk mounting flange 10 side). The second sealing device 9 seals the opening on the other end side of the space between the inner ring 4 and the outer ring 3.

  FIG. 2 is a sectional view in the axial direction of the first sealing device 8 in a non-wearing state during use after incorporation after the seal member is incorporated into the slinger. The second sealing device 9 has the same structure as the first sealing device 8. The description of the second sealing device 9 is omitted from the description of the first sealing device 8.

  As shown in FIG. 2, the first sealing device (hereinafter simply referred to as a sealing device) 8 includes a sealing member 48 and a slinger 52, and the sealing member 48 includes a cored bar member 50 and an elastic member 51. .

  The core member 50 is formed in an annular shape and has an L-shaped cross section. The core metal member 50 includes a cylindrical axially extending portion 60 as a fixed portion and a radially extending portion 61. The axially extending portion 60 is fitted and fixed to the inner peripheral surface of the outer ring 3 (see FIG. 1, not shown in FIG. 2). The radially extending portion 61 extends substantially inward in the radial direction from the other end side in the axial direction on the inner peripheral surface of the axially extending portion 60 (the left side in the drawing of FIG. 2).

  The slinger 52 is formed in an annular shape and has an L-shaped cross section. The slinger 52 has a cylindrical fixing portion 65 and a flange portion 66 connected to the fixing portion 65. The inner peripheral surface 68 of the fixing portion 65 is fixed by being fitted on the outer peripheral surface of the inner shaft 2. Needless to say, in the second sealing device 9, the first race member to which the slinger is fixed is the inner ring 4. The flange portion 66 extends from the end portion on the outer side in the axial direction (the right side in the drawing) of the outer peripheral surface of the fixed portion 65 to the outer side in the substantially radial direction. The flange portion 66 is located outward in the axial direction of the hub unit with respect to the radially extending portion 61 of the cored bar member 50. Most of the flange portion 66 excluding a part on the inner side in the radial direction is opposed to the radially extending portion 61 in the axial direction through a gap.

  The elastic member 51 is formed in an annular shape, and the axially outward end surface of the radially extending portion 61 connected to the entire inner peripheral surface of the axially extending portion 60 and the radially extending portion 61 connected to the inner peripheral surface of the axially extending portion 60. It is fixed to the core metal member 50 so as to cover the entire surface. The elastic member includes a base 53, a first axial lip 54, a second axial lip 55, and an annular protrusion 56. Specifically, the elastic member 51 is made of a rubber material. As the rubber material, nitrile rubber, hydrogenated nitrile rubber, acrylic rubber, silicon rubber, or fluorine rubber is preferably used.

  The base portion 53 is disposed along the inner peripheral surface of the axially extending portion 60 and the end surface of the radially extending portion 61 on the outer side in the axial direction. The base portion 53 is fixed to the inner peripheral surface of the axially extending portion 60 and the outer end surface of the radially extending portion 61. The first axial lip 54 extends from the base 53 to the outer ring 3 (see FIG. 1) side and the axially outer side (flange portion 66 side).

  The second axial lip 55 is spaced radially from the first axial lip 54 on the radially inner shaft 2 (see FIG. 1) side (inward radial direction) of the first axial lip 54. Is located. The second axial lip 55 has a first portion 57, a second portion 58, and a bent portion 59.

  The first portion 57 extends from the base 53 to the radially inner shaft 2 side and the axially outward side, while the second portion 58 is radially outwardly 3 side and axially outward. Extends to the side. The bent portion 59 is located between the first portion 57 and the second portion 58 and connects the first portion 57 and the second portion 58. The bent portion 59 has a substantially V-shaped cross section (substantially U-shaped cross section). In the cross section in the axial direction, in the second axial lip 55, the tip of the bent portion 59 is located at the radially innermost side.

  Although not shown, in a state before the elastic member 51 of the seal member 48 is incorporated into the slinger 53, that is, in a state where the elastic member 51 is not receiving force from the slinger 53, The inner surface 90 is concave, while the radially inner surface 91 of the second portion 58 is a conical surface.

  In a state where the elastic member 51 does not receive a force from the slinger 53, the curvature of the inner surface 90 in the radial direction of the first portion 57 in the axial section is outward in the axial direction (on the flange portion 66 side). It grows as you go. Specifically, in a state where the elastic member 51 is not receiving a force from the slinger 53, the radially inner surface 90 of the first portion 57 is a substantially conical cone located on the base 53 side in the axial section. A surface portion and a portion composed of a part of a substantially spheroidal surface that is smoothly connected to the conical surface portion and has a curvature that increases toward the outside in the axial direction (flange portion 66 side); It is made up of.

  On the other hand, the radially inner surface 91 of the second portion 58 is differentiable from one end to the other end in the axial section in a state where the elastic member 51 is not receiving force from the slinger 53. The surface 91 is smoothly connected.

  The protrusion 56 is annular and extends from the base 53 in a substantially radial direction. As shown in FIG. 2, the protrusion 56 is positioned at a distance from the slinger 52 in a non-wearing state during use after installation. In the non-wearing state at the time of use, the radially inner end of the protruding portion 56 overlaps the fixing portion 65 of the slinger 52 in the axial direction. The distal end portion of the protruding portion 56 and the distal end portion of the fixing portion 65 of the slinger 52 opposite to the flange portion 66 side constitute a labyrinth seal. In this way, the sealing performance is improved.

  The first axial lip 54 and the second portion 58 of the second axial lip 55 are brought into contact with the flange portion 66 of the slinger 52 by relative rotation about the axial center between the seal member 48 and the slinger 52 during assembly. It comes to slide. In addition, as shown in FIG. 2, the second axial lip 55 is positioned at a radial interval with respect to the fixing portion 65 of the slinger 52 in the assembled state and in the non-wearing state after use. is doing.

  The bending portion 59 contacts the fixing portion 65 of the slinger 52 in a state where the pressing force of the second axial lip 55 against the flange portion 66 is reduced by a predetermined force or more due to the wear of the second portion 57 of the second axial lip 55. Thus, it slides on the fixed portion 65. In this state, the bent portion 59 plays a role as a radial lip (meaning that it is a contact radial lip that is not a labyrinth seal).

  In a state in which the pressing force of the second axial lip 55 against the flange portion 66 is reduced by a predetermined force or more due to wear of the second portion 57 of the second axial lip 55, the protruding portion 56 is in contact with the fixing portion 65 of the slinger 52. Located at a distance. Further, in a state where the pressing force of the second axial lip 55 against the flange portion 66 is reduced by a predetermined force or more, the radially inner tip of the protruding portion 56 overlaps the fixing portion 65 of the slinger 52 in the axial direction. Yes.

  In the space formed by the first axial lip 54, the second axial lip 55, and the slinger 52, or in the space where the second axial lip 55 and the slinger 52 face each other, an appropriate amount of grease is sealed or lubricated. It has been applied. By this grease, the sliding portion between the first axial lip 54 and the slinger 52 and the sliding portion between the second axial lip 55 and the slinger 52 are lubricated.

  FIG. 3 shows the positions of the slinger 52 and the sealing member 48 in a pre-use state (for example, when the sealing device is transported before being assembled into the hub unit of the above embodiment or when the sealing device of the above embodiment is assembled). It is sectional drawing which shows a relationship, and is sectional drawing which shows the positional relationship of the slinger 52 and the sealing member 48 after assembling in the direction in which the slinger 52 and the sealing member 48 approach between the slinger 52 and the sealing member 48. is there.

  As shown in FIG. 3, the distance between the flange portion 66 of the slinger 52 and the radially extending portion 61 of the cored bar member 50 is closer between the slinger 52 and the seal member 48 than in use. After the arrangement, the protruding portion 56 comes into contact with the fixing portion 65 of the slinger 52 in a substantially stationary state.

  As shown in FIG. 3, in the state before use, the protruding portion 56 comes into contact with the fixing portion 65 of the slinger 52 in a state bent toward the flange portion 66 side of the slinger 52 in the axial direction.

  FIG. 4 shows the contact load ratio with respect to the total contact load of each lip when the lip is in a non-wearing state in each of the comparative sealing device and the sealing device of the above embodiment in one experimental example. It is a figure which shows ratio of the total contact load of the sealing device of the said embodiment with respect to the total contact load of the sealing device 270 of a comparative product.

  Here, the comparative sealing device 270 is a so-called pack-seal type sealing device having a cored bar member 250, an elastic member 251 and an L-shaped slinger 252 shown in FIG. 271 and a sealing device having two radial lips (a main lip 272 and an auxiliary lip 273).

  FIG. 7 shows a position where the elastic member 251 is present at the assembly position of the elastic member 251 when it is assumed that the elastic member 251 does not receive a force from the slinger 252 in the sealing device 270 of the comparative example.

  As shown in FIG. 4, in the comparative sealing device 270, the contact load ratio with respect to the total contact load of the radial lip (two in total) reaches 80%, whereas the contact load ratio with respect to the total contact load of the axial lip Is about 20%. From this, if the contact load of the radial lip can be reduced, the torque can be greatly reduced.

  Therefore, in the sealing device of the above embodiment that has only two axial lips and does not have a radial lip, the contact load ratio of the total contact load to the total contact load of the comparative product has reached only 40%, The contact load can be drastically reduced.

  FIG. 5 is a diagram showing the relationship between the rotational speed and the rotational torque in each of the comparative sealing device 270 and the sealing device of the embodiment in one experimental example.

  The torque of the sealing device of the above embodiment relative to the comparative product is about 50% of the torque of the sealing device of the comparative product from the region where the rotational speed is low to the high region. That is, the torque of the sealing device of the above embodiment is rapidly reduced as compared with the comparative product. This test was performed without using a lubricant (such as grease) in the sealing device of the above embodiment and the comparative sealing device 270.

  According to the sealing device of the above embodiment, the second axial lip 55 is fixed to the fixing portion 65 of the slinger 52 in the non-wearing state after use after the seal member 48 is incorporated into the slinger 52. The protrusions 56 are positioned at a distance from each other in the radial direction, and the protrusion 56 is positioned at a distance from the slinger 52, so that there is no radial lip that contacts the fixing part 65 of the slinger 52. Therefore, in the non-wearing state, the torque can be drastically reduced, and the fuel consumption of an automobile or the like having this sealing device can be reduced.

  Further, in the sealing device of the above embodiment, compared with the configuration in which the radial contact lip exists in the non-wearing use state, the contact lip in the radial direction does not exist in the non-wearing use state. While it can be reduced, the frictional force in the axial direction due to the absence of the radial contact lip is eliminated, and the slinger is put into a state before use such as when the sealing device is transported before being assembled into the hub unit or when the sealing device is assembled. With respect to 52, the seal member 48 may easily move in the axial direction.

  The seal member 48 and the slinger 52 are disposed so as to have an axial interval shorter than the axial interval between the radially extending portion and the flange portion in the non-wearing use state in a state before use. In this pre-use state, the protruding portion 56 comes into contact with the fixing portion 65 of the slinger 52 in a substantially stationary state. Therefore, the protruding portion 56 is fixed to the slinger 52 in the pre-use state. The portion 65 can be brought into contact with the portion 65 in a substantially stationary state. Therefore, it is possible to prevent the sealing member 48 from separating from the slinger 52 in the state before use.

  Further, according to the sealing device of the embodiment, the protruding portion 56 has a portion that is located at an interval from the slinger 52 and overlaps the fixing portion 65 of the slinger 52 in the axial direction in the non-wearing state. In the non-wearing state, the protruding portion 56 and the fixing portion 65 of the slinger 52 constitute a labyrinth seal. Therefore, the sealing performance can be improved in the non-wearing state.

  Moreover, according to the sealing device of the said embodiment, the said sealing member 48 and the said slinger 52 are axial directions between the said radial direction extension part in the said non-wearing use state and the said flange part in the state before use. In this pre-use state, the projecting portion 56 is bent toward the flange portion 66 side of the slinger 52 in the pre-use state, and substantially fixed to the fixing portion 65 of the slinger 52. Since the stationary portion 65 comes into contact with the fixing portion 65 of the slinger 52 in this state, in this state, the projecting portion 56 exerts a force from the fixing portion 65 of the slinger 52 to the flange portion 66 side, that is, the anti-scattering side. Will receive. Therefore, in the pre-use state such as during transportation, it is possible to increase the scatter prevention force.

  Further, according to the sealing device of the above embodiment, the protruding portion 56 in contact with the fixing portion 65 of the slinger 52 is moved in the axial direction to the side opposite to the flange portion 66 side to fix the slinger 52. When making no contact with the portion 65, the protruding portion 56 is not reversed, and the protruding portion 56 is not damaged.

  Further, according to the sealing device of the above-described embodiment, the bending portion 59 is in a state where the pressing force of the second axial lip 55 against the flange portion 66 is reduced by a predetermined force or more due to wear of the second portion 58 of the second axial lip 55. However, even if the wear of the second axial lip 55 is accelerated, the bent portion 59 as the radial lip is externally connected to the fixing portion 65 of the slinger 52. Thus, foreign matter such as muddy water can be prevented from entering the rolling element arrangement space of the hub unit.

  Further, according to the hub unit of the above embodiment, since the sealing device of the above embodiment is provided, the torque of the sealing device can be reduced during operation, and the fuel consumption of the vehicle having the hub unit of the present invention can be reduced. can do. Further, according to the present invention, since the sealing device of the present invention is provided, it is ensured that the slinger 52 and the seal member 48 are separated in a pre-use state such as during transportation before being assembled into the hub unit. Can be prevented.

  In the sealing device of the above embodiment, the protruding portion 56 protrudes substantially in the radial direction. However, in the present invention, the protruding portion 56 moves toward the axially flange portion 66 as it goes inward in the radial direction. You may protrude so that it may incline.

  Further, in the above hub unit, the sealing device of the present invention is disposed in the vicinity of the openings on both sides in the axial direction of the ball arrangement space (lubricant enclosure space). It may be arranged only in the vicinity of the opening on one side in the axial direction of the moving body (not a ball, but may be a roller, or both may be a ball) arrangement space (lubricant enclosure space) .

  FIG. 6 is an enlarged cross-sectional view of the periphery of the sealing device 99 of the water pump which is an embodiment of the rolling bearing device of the present invention including the sealing device 99 of the present invention.

  This water pump has a pump shaft 100 as a first track member, a mechanical seal 101, a pump housing 102, an outer ring 105 as a second track member, and the sealing device 99 of the present invention. The pump housing 102 has a drain hole 107 that penetrates the pump housing 102. The outer ring 105 is fitted and fixed to the inner peripheral surface of the pump housing 102.

  The pump shaft 100, the outer ring 105, and the sealing device 99 form part of a water pump bearing of the water pump. That is, although not shown, on the side indicated by the arrow a in FIG. 6 on the inner peripheral surface of the outer ring 105, a deep groove type raceway groove and a cylindrical raceway surface are spaced from each other in the axial direction and are closer to the sealing device 99. 6 is formed on the outer peripheral surface of the pump shaft 100 as indicated by an arrow a in FIG. 6 from the side closer to the sealing device 99 at an axial interval, and a deep groove type track groove and a cylindrical track. A surface is formed.

  Between the raceway groove of the outer ring 105 and the raceway groove of the pump shaft 100, a plurality of balls as rolling elements held in a cage are arranged at predetermined intervals in the circumferential direction. Yes. Further, between the cylindrical raceway surface of the outer ring 105 and the cylindrical raceway surface of the pump shaft 100, cylindrical rollers as rolling elements held by a cage are spaced apart at a predetermined interval in the circumferential direction. Are arranged.

  The cored bar portion 150 of the sealing device 99 is fitted and fixed to the inner peripheral surface of the outer ring 105, while the slinger 152 of the sealing device 99 is fitted and fixed to the outer peripheral surface of the pump shaft 100. Yes. The sealing device 99 seals the opening on the mechanical seal 101 side between the outer ring 105 and the pump shaft 100. In this manner, the cooling water in the pump chamber leaking from the mechanical seal 101 in the direction indicated by the arrow b is prevented from entering the water pump bearing.

  The leaked cooling water in the pump chamber is surely discharged to the outside in the direction indicated by the arrow c through the drain hole 107 formed in the pump housing 102. In FIG. 6, reference numeral 111 denotes a rubber sleeve of the mechanical seal 101, and 110 denotes a coil spring of the mechanical seal 101.

  If the sealing device 99 of the present invention is installed in the water pump as in the water pump shown in FIG. 6, the torque of the water pump bearing in the water pump can be reduced, and the fuel consumption of an automobile or the like having the water pump can be reduced.

  Further, according to the water pump of the above embodiment, the projecting portion 156 of the sealing device 99 is in a state before use such as when the sealing device 99 is assembled before being assembled into the water pump incorporating the sealing device 99. The seal member 148 and the slinger 152 are disposed so as to have an axial interval shorter than the axial interval between the radially extending portion and the flange portion in the non-wearing state. In the state, the protruding portion 156 comes into contact with the fixing portion 165 of the slinger 152 in a substantially stationary state. Therefore, the protruding portion 156 is substantially stationary on the fixing portion 165 of the slinger 152 in the pre-use state. It can be made to contact in the state. Therefore, it is possible to prevent the sealing member 148 from separating from the slinger 152 in the pre-use state.

  In the above embodiment, the sealing device of the present invention is set to a hub unit or a water pump. However, the sealing device of the present invention may be set between the rotor and the stator in the motor, and in this case, the operating cost of the motor can be reduced. The sealing device of the present invention may be disposed between the inner ring and the outer ring of a simple rolling bearing. The sealing device of the present invention includes a first member having an inner peripheral surface and a second member having an outer peripheral surface, and the first member and the second member are included in the first member. The device can be installed in any machine as long as it is a device facing the radial direction of the peripheral surface. And while being able to reduce the operating cost of the machine which installed the sealing device of this invention, it can prevent that a sealing device spreads in the machine.

It is sectional drawing of the axial direction of the hub unit which is one Embodiment of the rolling bearing apparatus of this invention. It is sectional drawing of the axial direction of the 1st sealing device in the non-wearing state at the time of use after incorporation after a seal member was incorporated in a slinger. It is sectional drawing of the axial direction of the 1st sealing device which shows the positional relationship of a slinger and a sealing member at the time of non-use. In one experimental example, the ratio of the contact load to the total contact load of each lip in each of the comparative sealing device and the sealing device of the above embodiment, and the sealing device of the above embodiment with respect to the total contact load of the comparative sealing device. It is a figure which shows ratio of all the contact loads. It is a figure which shows the relationship between the rotation speed and rotational torque in each of the sealing device of the said comparative product and the sealing device of the said embodiment in one experimental example. It is an expanded sectional view around the above-mentioned sealing device of a water pump which is one embodiment of the rolling bearing device of the present invention provided with the sealing device of the present invention. It is an expanded sectional view of the whole sealing device of a comparative product.

Explanation of symbols

2 Inner shaft 3 Outer ring 4 Inner ring 5 First ball 6 Second ball 8 First sealing device 9 Second sealing device 48,148 Seal member 50,150 Core metal member 51,151 Elastic member 52,152 Slinger 53 Base 54 First axial lip 55 Second axial lip 56,156 Protruding portion 57 First portion 58 Second portion 59 Bending portion 60 Axial extending portion 61 Radial extending portion 65,165 Fixed portion 66 Flange portion 99 Sealing device

Claims (2)

Seal member having a cylindrical fixing part, a cored bar member having a radially extending part extending from the fixing part in a substantially radial direction of the fixing part, and an elastic member fixed to the cored bar member When,
A slinger having a cylindrical fixing portion and a flange portion extending substantially in the radial direction from the fixing portion;
The elastic member is
A base fixed to the radially extending portion of the core member;
A first axial lip extending from the base and sliding on the flange;
Non-wearing state during use after assembly after the seal member is incorporated in the slinger while being positioned between the first axial lip and the fixed portion of the slinger and sliding on the flange portion A second axial lip located at a distance from the fixed portion of the slinger;
It consists of an annular protrusion that protrudes from the base,
The protrusion has a portion that is positioned at an interval from the slinger in the non-wearing state at the time of use and overlaps the fixed portion of the slinger in the axial direction.
The seal member and the slinger have an axial interval that is shorter than an axial interval between the radially extending portion and the flange portion during the use in a state before use before the use. Arranged so that
The protruding portion is in contact with the fixing portion of the slinger in a state in which the protruding portion is bent toward the flange portion of the slinger in the axial direction and is substantially stationary with respect to the fixing portion of the slinger in the pre-use state. A sealing device characterized in that A first race member having a raceway surface;
A second race member having a raceway surface;
A plurality of rolling elements disposed between the raceway surface of the first raceway member and the raceway surface of the second raceway member;
A rolling bearing device comprising: the sealing device according to claim 1 that seals an opening on one side in an axial direction between the first race member and the second race member.

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