JP2006064165A - Center bearing support mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a center bearing support mechanism capable of securely preventing foreign matters from entering into a clearance formed between an inner ring and an an inner ring. <P>SOLUTION: This center bearing support mechanism comprises the pair of inner rings 16 and 18 in which bearings 14 are disposed in their radial inner sides and disposed along the axial direction of the bearings through a first clearance T, a pair of outer rings 20 and 22 disposed on the radial outer sides of the pair of inner rings 16 and 18 and disposed along the axial direction of the bearings through a second clearance Q, a pair of elastic members 24 and 26 disposed between the pair of inner rings 16 and 18 and the pair of outer rings 20 and 22 so as to connect them to each other, and a seal means L preventing foreign matters from entering into the bearings 14. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a center bearing support mechanism that rotatably and elastically supports a propeller shaft in an automobile or the like.

  As shown in FIG. 4, as a conventional center bearing support mechanism 100, a ball bearing 102 into which a propeller shaft (not shown) is inserted, and an axial direction of the propeller shaft provided on the outer peripheral side (radially outer side) of the ball bearing 102 A pair of inner rings 104 and 106 arranged with a first gap T on the outer periphery, and a second gap Q in the axial direction of the propeller shaft provided on the outer peripheral side (radially outer side) of the inner rings 104 and 106. Bellows disposed between the inner rings 104 and 106 and the outer rings 108 and 110 and vulcanized and bonded to the inner rings 104 and 106 and the outer rings 108 and 110, respectively. One having a pair of elastic members 112 and 114 having a shape is known (see Patent Document 1 below).

    The center bearing support mechanism 100 is subjected to balance adjustment for adjusting the rotational unbalance of the propeller shaft (not shown) prior to being mounted on the automobile. That is, in this balance adjustment, as shown in FIG. 5, the center bearing support mechanism 100 disposed in the substantially middle portion of the propeller shaft 124 installed between the mission-side joint 120 and the differential-side joint 122 is cured. The load cell 126 is connected and fixed by a tool (not shown), the propeller shaft 124 is rotated at a high speed to unmeasure the unbalance of the propeller shaft 124, and a weight is attached to the propeller shaft 124 based on the measurement result. Thus, the unbalance of the propeller shaft 124 is corrected.

By the way, in order to fix and support the center bearing support mechanism with a jig, the second gap Q for inserting the jig is always formed between the outer ring 108 and the outer ring 110 in order to perform the balance adjustment. Must.
In addition, it is better not to form the first gap T between the inner ring 104 and the inner ring 106, but when the center bearing support mechanism 100 is assembled, press-fitting into the ball bearing 102 due to variations in component dimensions or the like. The first gap T is formed between the inner ring 104 and the inner ring 106 because of incompleteness and ease of positioning management in the axial direction of the propeller shaft when the ball bearing 102 is press-fitted. Is formed.
Registered Utility Model No. 2586021

  However, if gaps are formed between the outer ring and the outer ring or between the inner ring and the inner ring, water or the like enters the ball bearing from the outer ring side through the gaps, and the ball bearing is rusted. There is a risk that. If the ball bearing rusts, there will be a problem of adversely affecting the rotation of the propeller shaft. This is not limited to water, and if there is a gap, foreign matter such as dust enters from the gap, which adversely affects the rotation performance of the ball bearing and the rotation performance and durability of the propeller shaft.

  Therefore, in consideration of the above circumstances, the present invention can prevent foreign matters such as water and dust from entering the inner race side of the bearing through the outer race of the bearing from the gap formed between the inner ring and the inner ring. An object is to provide a bearing support mechanism.

  According to the first aspect of the present invention, a pair of inner rings disposed along the bearing axial direction with a first gap between the bearings disposed radially inward, and radially outward of the pair of inner rings. And a pair of outer rings disposed along the bearing axial direction with a second gap, and disposed between the pair of inner rings and the pair of outer rings. It has a pair of elastic members and sealing means for preventing foreign matter from entering the bearing.

According to the first aspect of the present invention, the pair of inner rings in which the bearings are arranged on the radially inner side are arranged along the bearing axial direction with the first gap, and the pair of outer rings is a pair. The inner ring is disposed radially outside and disposed along the bearing axial direction with a second gap, and the pair of elastic members are disposed between the pair of inner rings and the pair of outer rings. Arranged to connect. In this way, the structure constituted by the inner ring, the elastic member, and the outer ring is arranged along the bearing axial direction.
Here, since the sealing means for preventing foreign matter from entering the bearing is provided, foreign matter that has entered from the second gap can be further prevented from entering the inner race side of the bearing from the first gap. Thereby, it can prevent that a foreign material exerts a bad influence on the rotational performance of a ball bearing or the rotational performance of a propeller shaft.
In the present invention, the term “foreign matter” means all things that are fixed and liquid at room temperature, such as dust, dust, and water.

  According to a second aspect of the present invention, in the center bearing support mechanism according to the first aspect, the sealing means is a liquid packing filled so as to close the first gap.

According to the second aspect of the present invention, since the first gap is filled with the liquid packing as the sealing means and the first gap is closed, it is possible to reliably prevent foreign matter from entering the bearing. Can do.
Further, when the first gap is closed by the liquid packing, the internal bearing cannot be visually recognized from the outside through the first gap, so that the design of the center bearing support mechanism can be improved.

  According to a third aspect of the present invention, in the center bearing support mechanism according to the first or second aspect, the sealing means is a liquid packing filled between the inner ring and the bearing. .

According to the third aspect of the present invention, since the liquid packing as the sealing means is filled between the inner ring and the bearing, it is possible to reliably prevent foreign matter from entering the bearing.
In particular, the sealing performance can be significantly improved by closing the first gap with the liquid packing and filling the liquid packing between the inner ring and the bearing.

  According to a fourth aspect of the present invention, in the center bearing support mechanism according to the second or third aspect, a groove for storing the liquid packing is formed on an inner peripheral surface of the inner ring facing the bearing. It is characterized by being.

  According to the fourth aspect of the present invention, since the groove for storing the liquid packing is formed on the inner peripheral surface facing the bearing of the inner ring, a large amount of liquid packing is provided between the inner ring and the bearing. Can be filled. Thereby, sealing performance can be improved significantly.

  According to a fifth aspect of the present invention, in the center bearing support mechanism according to any one of the second to fourth aspects, the liquid packing is an elastic adhesive.

  According to the fifth aspect of the present invention, by using an elastic adhesive as the liquid packing, it is possible to give elasticity performance in addition to sealing performance, so that vibration acting on the center bearing support mechanism can be absorbed. it can.

  The invention according to claim 6 is the center bearing support mechanism according to any one of claims 1 to 5, wherein the pair of inner rings, the pair of outer rings, and the pair of elastic members are: Each of them has the same shape.

  According to the invention described in claim 6, by making the pair of inner rings, the pair of outer rings, and the pair of elastic members the same shape, each inner ring, the outer ring, and the elastic part can be shared. The center bearing support mechanism can be manufactured. This eliminates the need to manufacture differently shaped inner rings, outer rings, and elastic members, thus reducing the number of parts for each component, reducing the manufacturing cost without the need to manufacture new molds, and managing parts. Is also easier.

  According to the present invention, since the sealing means is provided, it is possible to prevent foreign matters such as water and dust that have entered from the second gap from further entering the bearing side. Thereby, it is possible to easily prevent foreign matters such as water and dust from deteriorating the rotational performance of the ball bearing and adversely affecting the rotational performance of the propeller shaft.

  Next, a center bearing support mechanism according to an embodiment of the present invention will be described with reference to the drawings.

  As shown in FIGS. 1 and 2, the center bearing support mechanism 10 includes a ball bearing (bearing) 14 through which the propeller shaft 12 is inserted on the inner peripheral side (radially inward (direction of arrow I in FIG. 1)), Arranged with a first clearance T in the ball bearing axial direction (arrow X direction in FIG. 1) provided on the outer peripheral side (radially outer side (arrow O direction side in FIG. 1)) of the ball bearing (bearing) 14. A pair of inner rings 16, 18 are provided on the outer peripheral side (radially outward (arrow O direction side in FIG. 1)) of the inner rings 16, 18 and in the ball bearing axial direction (arrow X direction in FIG. 1). A pair of outer rings 20, 22 arranged with a second gap Q, and arranged between the inner rings 16, 18 and the outer rings 20, 22, are arranged between the inner rings 16, 18 and the outer rings 20, 22. A pair of rubber members each having a bellows shape that is vulcanized and bonded ( And outer ring holding brackets 28 arranged on the outer peripheral side (radially outer side (arrow O direction side in FIG. 1)) of the outer rings 20 and 22 and fixed to the vehicle body side. Yes.

  The ball bearing (bearing) 14 includes a ball 14A, an inner race 14B that supports the ball 14A from the radially inner side (arrow I direction side in FIG. 1), and a ball 14A that is radially outward (arrow O direction side in FIG. 1). The outer race 14C is supported by the outer race 14C. The rotation of the ball 14A allows the inner race 14B to rotate in the circumferential direction with respect to the outer race 14C.

  The inner rings 16 and 18 are each formed in an annular shape, and projecting portions 16A and 18A projecting radially outward (arrow O direction side in FIG. 1) and the ball bearing axial direction (arrow X direction in FIG. 1). Inclined portions 16B and 18B that are inclined with respect to each other. Moreover, as shown in FIG. 2, each protrusion 16A, 18A includes radial extending portions 30A, 32A extending in the radial direction and axial extending portions 30B, 32B extending in the ball bearing axial direction. Yes. Further, a ball bearing 14 is press-fitted into each of the protrusions 16A and 18A. A first gap T having a predetermined dimension is formed between the end portions of the protrusions 16A and 18A.

Here, oblique side portions 34 and 36 that are inclined with respect to the radial direction are respectively formed at the axial one end portions of the axially extending portions 30B and 32B constituting the inner rings 16 and 18. In addition, a groove 38 in which the liquid packing L is stored is formed in a portion of the radially extending portion 30A that constitutes the one projecting portion 16A that faces the ball bearing 14. Further, a groove 40 in which the liquid packing L is stored is formed in a portion of the axially extending portion 32B that constitutes the other protruding portion 18A that faces the ball bearing 14.
Further, the first gap T formed between the axially extending portions 30B and 32B constituting the projecting portions 16A and 18A is filled with the liquid packing L, and the liquid packing L causes the first gap T to be formed. The gap T is closed. Further, the liquid packing L is similarly filled between the axially extending portions 30B and 32B and the outer race 14C of the ball bearing 14. Further, the liquid packing L is similarly filled between the radially extending portions 30 </ b> A and 32 </ b> A and the outer race 14 </ b> C of the ball bearing 14.
As the liquid packing, an adhesive having a high elasticity is optimal, but the liquid packing is not limited to an adhesive, and may be a well-known liquid packing such as an elastic resin such as rubber or silicone.

  The rubber members (elastic members) 24 and 26 are vulcanized and bonded to the outer peripheral surfaces of the inner rings 16 and 18 and the inner peripheral surfaces of the outer rings 20 and 22, respectively. The rubber members 24 and 26 include inner base portions 24A and 26A that are vulcanized and bonded to the inner rings 16 and 18, spring portions 24B and 26B that protrude greatly toward one side in the axial direction, and outer rings 20 and 22 respectively. The outer base portions 24C and 26C are vulcanized and bonded to each other. Moreover, each rubber member 24 and 26 is shape | molded so that it may become the same shape.

  The outer rings 20 and 22 are disposed on the outer peripheral surfaces of the outer base portions 24C and 26C constituting the rubber members 24 and 26, respectively. The outer bases 24C and 26C are vulcanized and bonded to the outer rings 20 and 22, respectively. A second gap Q having a predetermined size is formed between the outer rings 20 and 22. Moreover, each outer ring 20 and 22 is shape | molded so that it may become the same shape (symmetrical arrangement | positioning).

  The bracket 28 is disposed on the outer peripheral surface of each of the outer rings 20 and 22, and is attached to the vehicle body side integrally with the outer ring holding ring body 29 by a fixing tool such as a bolt and a nut.

  Next, a method for assembling the center bearing support mechanism 10 will be described.

  First, the inner ring 16 (18) and the outer ring 20 (22) are positioned in a predetermined mold (not shown), and an unvulcanized rubber member 24 (26) is placed in a predetermined part of the mold. Pour. Then, the rubber member 24 (26) is vulcanized by heating, and vulcanized and bonded to the inner ring 16 (18) and the outer ring 20 (22), respectively, so that the inner ring 16 (18) and the outer ring 20 ( 22) and a support mechanism main body composed of the rubber member 24 (26). In this way, the support mechanism main body is manufactured one after another.

Next, the liquid packing L is applied to the inner peripheral surfaces of the projecting portions 16A and 18A constituting the inner rings 16 and 18, and the two support mechanism bodies are moved in the ball bearing axial direction. Thereby, the ball bearing 14 is press-fitted into the inner peripheral surfaces of the projecting portions 16A and 18A constituting the inner rings 16 and 18 of the support mechanism main bodies. When the ball bearing 14 is press-fitted into the inner peripheral surfaces of the protrusions 16A and 18A, a first gap T formed between the axially extending portions 30B and 32B constituting the protrusions 16A and 18A. Is closed by the liquid packing L, and between the radially extending portions 30A and 32A constituting the protruding portions 16A and 18A and the outer race 14C of the ball bearing 14, and the axially extending portions 30B and 32B. And the outer race 14C of the ball bearing 14 is filled with the liquid packing L.
As described above, in the method for assembling the center bearing support mechanism 10, the center bearing support mechanism 10 can be easily assembled and the first gap T can be reliably closed.

  Next, the operation of the center bearing support mechanism 10 will be described.

  As shown in FIG. 2, the first gap T formed between the inner rings 16 and 18 is closed by the liquid packing L, and the outer races of the radially extending portions 30 </ b> A and 32 </ b> A and the ball bearing 14. 14C and between the axially extending portions 30B and 32B and the outer race 14C of the ball bearing 14, the liquid packing L is filled. Even if the invading foreign material tries to enter the ball bearing 14 side from the first gap T, it is blocked by the liquid packing L. As a result, since foreign matter cannot enter the ball bearing 14 side, it is possible to prevent the ball bearing 14 from being rusted, and to reliably prevent the rotation function of the ball bearing 14 and the propeller shaft 12 from occurring. Can be prevented.

In particular, by forming the grooves 38, 40 for storing the liquid packing L in the inner rings 16, 18, the grooves 38, 40 can be filled with a large amount of the liquid packing L. The volume of the liquid packing L interposed between the outer race 14C of the ball bearing 14 and the ball bearing 14 is increased, so that the sealing performance can be remarkably improved. By staying in contact, peeling due to contact rubbing is prevented, and a reliable sealing property is maintained.
Further, since the oblique sides 34 and 36 are formed at the end portions of the axially extending portions 30B and 32B constituting the projecting portions 16A and 18A, respectively, the first gap T is increased, and the first Since the gap T can be filled with a large amount of liquid packing L, the sealing performance can be remarkably improved.
A configuration in which a plurality of grooves 38 and 40 are formed is preferable in terms of greatly improving the sealing performance, but it is effective if at least one groove is formed in a part of the inner ring 16 (18). .

  Further, by using an adhesive as the liquid packing L, elasticity performance can be obtained in addition to sealing performance, and vibrations acting on the center bearing support mechanism 10 can be absorbed.

  In addition, a first gap T is formed between the inner rings 16 and 18, but the ball bearing 14 cannot be visually recognized from the outside because it is closed by the liquid packing L. For this reason, the design and merchantability of the center bearing support mechanism 10 can be improved, and the anxiety of appearance when the ball bearing 14 can be visually recognized as in the past can be eliminated.

Next, a modified example of the center bearing support mechanism 10 will be described.
In FIG. 3, the same components as those in FIG. 2 are denoted by the same reference numerals, and description thereof will be omitted as appropriate.

As shown in FIG. 3, the formation site of the groove formed in each inner ring 16, 18 is not limited to the above embodiment, and for example, each radial extension portion 30 </ b> A, 32 </ b> A and each axial extension You may form the groove | channel 42 for accumulating the liquid packing L in the corner | angular part formed with the parts 30B and 32B.
In this way, by forming the groove 42 in the same part of each inner ring 16, 18, the same shape of the inner rings 16, 18, outer rings 20, 22 and rubber members 24, 26 can be mass-produced There is no need to manufacture differently shaped inner rings, outer rings, and elastic members using a separate mold. As a result, the number of parts can be reduced, and it is not necessary to separately manufacture a dedicated mold, the manufacturing cost of the center bearing support mechanism 10 can be reduced, and parts management is facilitated.

It is a block diagram of the center bearing support mechanism which concerns on one Embodiment of this invention. It is the enlarged view which showed the principal part of the center bearing support mechanism which concerns on one Embodiment of this invention. It is the enlarged view which showed the principal part of the modification of the center bearing support mechanism which concerns on one Embodiment of this invention. It is a fragmentary sectional view of the conventional center bearing support mechanism. It is explanatory drawing of the balance adjustment apparatus of a center bearing support mechanism.

Explanation of symbols

10 Center bearing support mechanism 14 Ball bearing (bearing)
16 Inner ring 18 Inner ring 20 Outer ring 22 Outer ring 24 Rubber member (elastic member)
26 Rubber member (elastic member)
38 groove 40 groove 42 groove T first gap Q second gap L liquid packing (sealing means)

Claims (6)

A pair of inner rings disposed along the axial direction of the bearing with a bearing disposed radially inside and having a first gap;
A pair of outer rings disposed radially outside the pair of inner rings and disposed along the bearing axial direction with a second gap;
A pair of elastic members arranged to connect the pair of inner rings and the pair of outer rings;
Sealing means for preventing foreign matter from entering the bearing;
A center bearing support mechanism characterized by comprising:   The center bearing support mechanism according to claim 1, wherein the sealing means is a liquid packing filled so as to close the first gap.   The center bearing support mechanism according to claim 1 or 2, wherein the sealing means is a liquid packing filled between the inner ring and the bearing.   The center bearing support mechanism according to claim 2 or 3, wherein a groove for storing the liquid packing is formed on an inner peripheral surface of the inner ring facing the bearing.   The center bearing support mechanism according to any one of claims 2 to 4, wherein the liquid packing is an elastic adhesive.   The center bearing support mechanism according to any one of claims 1 to 5, wherein the pair of inner rings, the pair of outer rings, and the pair of elastic members have the same shape.

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