CN1126876C

CN1126876C - Ball bearing

Info

Publication number: CN1126876C
Application number: CN00105451A
Authority: CN
Inventors: 坂口智也; 赤松良信
Original assignee: NTN Corp
Current assignee: NTN Corp
Priority date: 1999-04-07
Filing date: 2000-04-05
Publication date: 2003-11-05
Anticipated expiration: 2020-04-05
Also published as: JP2000291662A; CN1269475A

Abstract

The invention provides a bearing capable of reducing the deformation of a cage caused by the centrifugal force while using an inexpensive crown-shaped cage, and capable of being used under high speed rotation. A rolling element 3 is placed between an inner ring 1 and an outer ring 2, and held by a cage 4. The cage 4 has the shape of a crown, and one side surface of an annular body 6 has a pocket 5 partially opened for holding the rolling element 3 inside. A pitch circular diameter PCD of the pocket 5 of the cage 4 is larger than a center Q of a radial thickness of a circumferential wall cross section of the annular body 6.

Description

Ball bearing

Technical field

The present invention relates to the required ball bearing of high rotating speed, particularly be called as the improvement of crown shape seat ring.

Background technique

Household appliances or various machinery for reason such as reducing cost, adopt the ball bearing with crown shape seat ring mostly.For example, the motor that vacuum cleaner is used in order to improve suction, is realized miniaturization, just needs to improve its maximum speed.This motor generally all adopts the chute-type ball bearing about internal diameter 8mm.

The seat ring of this ball bearing, the past is adopted the waveform seat ring that is made of annular iron plate parts, is replaced by resin system crown shape seat ring cheaply now.This crown shape seat ring can be made at low cost with injection moulding method, moreover, because when ball bearing is assembled, as long as seat ring is inserted between the raceway circle that circumferencial direction disposing ball equidistantly, so the assembly expenses of bearing also can reduce.

But, crown shape seat ring be shaped as left and right sides asymmetry, resinous and metal comparing is out of shape because of being subjected to external force easily.Therefore, when using under high rotating speed, seat ring is out of shape because of external force easily, is difficult to rotate swimmingly.

Summary of the invention

The purpose of this invention is to provide a kind of energy and adopt cheap crown shape seat ring, can reduce the seat ring distortion that centrifugal force causes simultaneously again, the ball bearing that can under higher rotating speed, rotate.

The invention provides a kind of ball bearing, it is a kind of ball bearing with the seat ring that remains in the rolling element between inner ring and the outer ring, this seat ring is that some opens at the seat ring that above-mentioned annular solid one side, inside are keeping the nest groove of rolling element at a plurality of positions of annular solid circumferencial direction, and the pitch diameter of the nest groove of above-mentioned seat ring is greater than the center of above-mentioned annular solid perisporium cross-section radial thickness; Wherein, the radial thickness in the perisporium cross section of the annular solid of above-mentioned seat ring is taked the shape that gradually reduces from the open side of nest groove bottom one side direction nest groove.

Nest groove bottom periphery at the outer diametric plane of the annular solid of above-mentioned seat ring forms flange.

Above-mentioned seat ring between the nest groove of annular solid part, be to have in the post portion from the end face recess of front end to base portion depression.

Above-mentioned seat ring between the nest groove of annular solid part, be the side face recess that has in the post portion from the outer diametric plane of annular solid or aperture surface depression.

Above-mentioned seat ring is the molded products of the mixture of synthetic resin or synthetic resin and fiber formation.

Above-mentioned seat ring is the molded products of the synthetic resin mixture of synthetic resin, fiber and lubricant oil formation.

The distortion that crown shape seat ring causes because of centrifugal force is by the twisting strength that constitutes nest bottom land wall section (rigidity) and act on part between the nest groove, be that the centrifugal force of post portion is determined.As mentioned above, as the pitch diameter of the nest groove center greater than annular solid perisporium cross-section radial thickness, in other words, promptly perisporium section ratio pitch diameter more is partial to internal diameter one side, and then the sectional area of nest bottom land wall section increases, and the twisting strength of nest bottom land wall section improves.In addition, post portion is from the radius-zoom-out of bearing center of rotation, and the centrifugal force that acts on post portion reduces.Like this, seat ring can use under higher rotating speed because of the distortion that centrifugal force causes reduces.

Form flange by the nest groove bottom periphery at seat ring, the nest bottom land wall section sectional area of seat ring increases, and twisting strength is improved.Therefore, suppressed to act on the seat ring distortion that the centrifugal force of post portion causes.Because above-mentioned flange is arranged at outside diameter, so even seat ring is out of shape because of centrifugal force, flange also can be because of its distortion breaks away from the outer ring, can not slip and hinder rotation because of flange and outer ring, cause the wearing and tearing of seat ring.

The radial thickness in the perisporium cross section by making the race body is taked the shape that gradually reduces from the open side of nest groove bottom one side direction nest groove, increasing requirement has the sectional area of the nest bottom land wall section of certain twisting strength, reduce the quality of post portion front end by the requirement that reduces centrifugal force, like this, by improving twisting strength and reducing the better effects if that centrifugal force prevents the seat ring distortion.

By in post portion, offering the end face recess, reduced by the quality of the post portion of centrifugal action, the distortion that produces because of centrifugal force can further obtain reducing.

By in post portion, offering the side face recess, reduced by the quality of the post portion of centrifugal action, the distortion that produces because of centrifugal force can further obtain reducing.

Even the molded products of the single synthetic resin mixture made from synthetic resin of seat ring also can suppress the distortion that causes because of centrifugal force because of said structure of the present invention.Because single mixture with synthetic resin is so cost of production is lower.

As seat ring is the molded products of the synthetic resin mixture of synthetic resin and fiber formation, and then because of the reinforing function of fiber, the intensity of seat ring is improved, and can reduce the distortion that centrifugal force causes better.

In the present invention, seat ring can also be the molded products of the synthetic resin mixture of synthetic resin, fiber and lubricant oil formation.Like this, owing to contain lubricant oil in the synthetic resin mixture, the greasy property during therefore high rotating speed in the ball bearing is improved.Because fibre-bearing is so the intensity of seat ring also is improved.

Description of drawings

Fig. 1 is the partial cross section figure of the ball bearing of one embodiment of the present invention.

Fig. 2 is the stereogram of seat ring of the present invention.

Fig. 3 is the stereogram of seat ring remodeling.

Fig. 4 is the stereogram of the another kind of remodeling of seat ring.

Fig. 5 is the stereogram of another remodeling of seat ring.

Fig. 6 is the stereogram of another remodeling of seat ring.

Fig. 7 is the stereogram of another remodeling of seat ring.

Fig. 8 is the stereogram of another remodeling of seat ring.

Fig. 9 is the stereogram of another remodeling of seat ring.

Figure 10 is the stereogram of another remodeling of seat ring.

Figure 11 is the stereogram of another remodeling of seat ring.

Embodiment

Below, with reference to Fig. 1 and Fig. 2 an embodiment of the invention are described.This ball bearing as shown in Figure 1, between inner ring 1 and outer ring 2, is being provided with a plurality of rolling elements 3 at circumferencial direction side by side, and these rolling elements 3 are being kept by so-called crown shape seat ring 4.Inner ring 1 has rolling element 3 raceway ditch that roll, cross section circular arc (roller surface) 1a, 2a thereon with outer ring 2, and this ball bearing is the chute-type ball bearing.Inside and outside circle 1,2 and rolling element 3 are by making such as steel etc., and seat ring 4 is molded productss of synthetic resin mixture.

Shown in the stereogram of Fig. 2, seat ring 4 has a plurality of positions to have the nest groove 5 that inside is keeping rolling element 3 at the circumferencial direction of annular solid 6.The part of opening of each nest groove 5 is in an axial end of annular solid 6 one sides.The inside of each nest groove 5 is along the curvecd surface type of the concave spherical of the outside of rolling element 3.Part between the

adjacent nest groove

5,5 of annular solid 6 is a post portion 7.

In this embodiment, has the pitch diameter PCD of nest groove 5 shown in Figure 1 of seat ring 4 of this structure greater than the diameter of the center Q of the formation perisporium cross-section radial thickness of annular solid 6.Therefore, from the corresponding position of pitch diameter PCD of seat ring 4 radial thickness H to the seat ring aperture surface, with the pass of the whole radial thickness W of seat ring 4 be

H＞W/2。

The outer diametric plane of seat ring 4 and aperture surface are the cylndrical surface.The pitch diameter PCD of nest groove 5 is for the diameter of a circle at the center by remaining on the rolling element 3 in each nest groove 5, and is such in this example, and nest groove 5 the insides are the diameter of a circle that is under the situation of sphere shape by the centre of curvature inside the sphere shape of each nest groove 5.

Employing has this configured balls bearing, and the distortion that the seat ring 4 that produces along with the rotation of bearing causes because of centrifugal force is determined by the twisting strength of nest bottom land wall section 6a and the centrifugal force that acts on post portion 7.In this embodiment, the pitch diameter PCD of nest groove 5 is greater than the center Q of annular solid 6 perisporium cross-section radial thickness, perisporium section ratio pitch diameter PCD more is partial to internal diameter one side, therefore, compare with the consistent crown shape seat ring of pitch diameter PCD with the center in general perisporium cross section, the sectional area of nest bottom land wall section 6a increases, and post portion 7 is from the radius-zoom-out of bearing center of rotation.Therefore, the twisting strength of nest bottom land wall section 6a is improved, and the centrifugal force that acts on post portion 7 reduces.Like this, seat ring 4 can use under higher rotating speed because of the distortion that centrifugal force causes reduces.

Fig. 3 to Figure 11 represents is the various remodeling of the used seat ring 4 of ball bearing shown in Figure 1.Earlier the common structure to the seat ring 4 of these remodeling describes, and any remodeling all has the nest groove 5 that inside is keeping rolling element 3 at a plurality of positions of the circumferencial direction of annular solid 6, and the part of opening that is equipped with nest groove 5 is in a side of annular solid 6.The inside of each nest groove 5 is along the curvecd surface type of the concave spherical of the outside of rolling element 3.Part between the

adjacent nest groove

5,5 of annular solid 6 is a post portion 7.In addition, all the example with shown in Figure 1 is the same for any one, and the pitch diameter PCD of the nest groove 5 of seat ring 4 is greater than the center Q of annular solid 6 perisporium cross-section radial thickness.

The remodeling seat ring 4 of Fig. 3 is the nest groove bottom periphery formation flanges 8 at the outer diametric plane of annular solid 6.By forming flange 8, the outside dimension of the nest groove open sides of annular solid 6 is littler than the outside dimension of nest groove bottom side.

Under the situation of this formation flange 8, by forming flange 8, the nest bottom land wall section sectional area of seat ring 4 increases, and twisting strength is improved.Therefore, acting on seat ring 4 distortion that the centrifugal force of post portion 7 causes further obtains reducing.In addition, because flange 8 is arranged at outside diameter, so the front end in post portion 7 bends towards external diameter one side because of being subjected to centrifugal force, make seat ring 4 be out of shape, flange 8 also can be out of shape to the direction that breaks away from the outer ring because of its described deformation force, can not slip and hinder rotation, cause the wearing and tearing of seat ring 4 because of flange 8 and outer ring 2.

Under the situation that is provided with flange 8, the pitch diameter PCD (Fig. 1) of the nest groove 5 of seat ring 4 can be consistent except the center of the perisporium cross-section radial thickness of flange 8 with annular solid 6.

The perisporium cross-section radial thickness d of the annular solid 6 of the remodeling seat ring 4 of Fig. 4 has been taked to open the shape that the side 4b of a side gradually reduces from the side 4a of nest groove bottom one side to the nest groove.Specifically, the outer diametric plane of annular solid 6 is the conical surface that diameter progressively dwindles to the side 4b of nest groove open sides, and its aperture surface is the cylndrical surface.In addition, the inside and outside the inside of annular solid 6 can be conical surface.

Like this, because the perisporium cross-section radial thickness d of seat ring 4 has been taked to open the shape that the side 4b of a side gradually reduces from the side 4a of nest groove bottom one side to the nest groove, therefore increased the sectional area of the nest bottom land wall section that requires to have certain twisting strength, the quality that has reduced post portion front end by the requirement that reduces centrifugal force is arranged simultaneously, like this, by improving twisting strength and reducing the better effects if that centrifugal force prevents the seat ring distortion.

The remodeling seat ring 4 of Fig. 4 can also be further as shown in Figure 5, forms flange 8 at the nest groove bottom periphery of the outer diametric plane of annular solid 6.

The remodeling seat ring 4 of Fig. 6 is in part between the nest groove of annular solid 6, is to have in each post portion 7 from the end face recess 9 of front end to base portion depression.The degree of depth of end face recess 9 is greater than the axial depth of nest groove 5.In addition, also form flange 8 at the nest groove bottom periphery of the outer diametric plane of annular solid 6.In more detail, the degree of depth of end face recess 9 reaches the lateral location of flange 8 always, and by forming end face recess 9, post portion 7 is divided into two at the seat ring circumferencial direction.Flange 8 not necessarily must be established.

Like this, by offer end face recess 9 in post portion 7, reduced by the quality of the post portion 7 of centrifugal action, the distortion that produces because of centrifugal force can further obtain reducing.

For the remodeling of Fig. 6, can be as shown in Figure 7, allow the degree of depth of its end face recess 9 less than the axial depth of nest groove 5.In the remodeling of Fig. 7, by forming end face recess 9, the fore-end of post portion 7 more than the bottom surface of end face recess 9 becomes a pair of claw type part 7a along the concave curved surface of nest groove the inside.

At end face recess 9 as shown in Figure 7, under the situation of its degree of depth less than the axial depth of nest groove 5, can be as respectively the retrofiting shown in the seat ring of Fig. 8, Fig. 9, allow the perisporium cross-section radial thickness of annular solid 6 of seat ring 4 take from the side of nest groove bottom one side to open the shape that the side of a side gradually reduces to the nest groove.The seat ring of respectively retrofiting of Fig. 8, Fig. 9 all can allow the outer diametric plane of annular solid 6 be conical surface, and aperture surface is the cylndrical surface.The remodeling of Fig. 8 is the remodeling that does not have the external diameter flange, and the remodeling of Fig. 9 is the remodeling that forms flange 8 at the nest groove bottom periphery of the outer diametric plane of annular solid 6.

In addition, also can be as Figure 10 or shown in Figure 11, seat ring 4 between the nest groove of its annular solid 6 part, be the side face recess 10 that has in the post portion 7 from the outer diametric plane depression of annular solid 6.

The remodeling of Figure 10 is the remodeling of Fig. 3, and promptly the outer diametric plane of annular solid 6 and aperture surface are the cylndrical surface, are provided with the remodeling of flange 8, and the remodeling of side face 10 recesses is set again.

The remodeling of Figure 11 is the remodeling of Fig. 5, and promptly the outer diametric plane of annular solid 6 is conical surfaces, and aperture surface is the cylndrical surface, and is provided with the remodeling of flange 8, and the remodeling of side face recess 10 is set again.

As Figure 10, remodeling shown in Figure 11, be provided with side face recess 10, reduced by the quality of the post portion 7 of centrifugal action, can further reduce the distortion that centrifugal force causes.

In addition, side face recess 10 also can be in post portion 7 be offered depression from the aperture surface of annular solid 6 and goes down.

Material to the seat ring 4 of the respective embodiments described above describes below.Seat ring 4 can be the molded products of single synthetic resin mixture made from synthetic resin, and in this case, cost of material is lower.

Seat ring 4 can also be the molded products of the synthetic resin mixture of synthetic resin and fiber formation, and in this case, because of the reinforing function of fiber, the intensity of seat ring is improved, and can reduce the distortion that centrifugal force causes better.The fiber that cooperates with seat ring 4 can be with carbon fiber etc.

In addition, seat ring 4 can also be the molded products of the synthetic resin mixture of synthetic resin, fiber and lubricant oil formation.In this case, except the stiffening effect of fiber, the greasy property during high rotating speed in the ball bearing is improved.

Ball bearing of the present invention has adopted cheap crown shape seat ring, can reduce the seat ring distortion that centrifugal force causes, and can use under higher rotating speed.

Claims

1. ball bearing with the seat ring that remains in the rolling element between inner ring and the outer ring, this seat ring is that some opens at the seat ring that above-mentioned annular solid one side, inside are keeping the nest groove of rolling element at a plurality of positions of annular solid circumferencial direction, and the pitch diameter of the nest groove of above-mentioned seat ring is greater than the center of above-mentioned annular solid perisporium cross-section radial thickness; It is characterized in that the radial thickness in the perisporium cross section of the annular solid of above-mentioned seat ring is taked the shape that gradually reduces from the open side of nest groove bottom one side direction nest groove.

2. ball bearing according to claim 1 is characterized in that, the nest groove bottom periphery at the outer diametric plane of the annular solid of above-mentioned seat ring forms flange.

3. ball bearing according to claim 1 and 2 is characterized in that, above-mentioned seat ring between the nest groove of annular solid part, be to have in the post portion from the end face recess of front end to base portion depression.

4. ball bearing according to claim 1 and 2 is characterized in that, above-mentioned seat ring between the nest groove of annular solid part, be the side face recess that has in the post portion from the outer diametric plane of annular solid or aperture surface depression.

5. ball bearing according to claim 1 and 2 is characterized in that, above-mentioned seat ring is the molded products of the mixture of synthetic resin or synthetic resin and fiber formation.

6. ball bearing according to claim 1 and 2 is characterized in that, above-mentioned seat ring is the molded products of the synthetic resin mixture of synthetic resin, fiber and lubricant oil formation.