KR101157350B1 - Split toroidal bearing - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a self-aligning free-form split bearing, in which a plurality of rollers are disposed between the outer circumference of the inner race of the split bearing and the inner circumference of the outer race, wherein the roller is provided with a bulge in the center thereof. The elliptic curve is formed in a cross section, and the raceway of the outer raceway of the inner race and the raceway of the inner raceway of the outer race is recessed into a curved cross section with a larger arc than the curved end of the roller. The left and right annular flanges, which are formed and serve as assembly members of the inner race, which protrude on both edges of the outer raceway of the inner race, are formed with a gap having a width greater than the length of the roller.
According to the present invention, the swelling portion of the roller is connected to the concave portion of the inner race and the outer race raceway to be carefully calibrated, and the inner race is left and right with respect to the outer race with the roller interposed therebetween in correspondence with the expansion and contraction of the shaft. Axial flow became possible.

Description

Self-Aligning Freestyle Split Bearings {SPLIT TOROIDAL BEARING}

The present invention relates to a self-aligning free-form split bearing in a bearing which is a mechanical element for lubricating a shaft.

In general, most long shafts, such as shafts of various mechanical mechanisms, metal shafts of paper rolls in paper mills, support shafts of rotating drums, and both ends of the shafts for bearing rotation, It is supported on the frame by bearing.

In the case of a large shaft having a length of 1.5 m to 2 m or more and a relatively large outer diameter, the shaft length (about 5 mm to 25 mm) changes by contraction and extension depending on the temperature. That is, as shown in Fig. 3, when the one end bearing bearing b1 of the shaft X is fixed to the P ₀ line position, the other bearing side bearing bearing b2 of the same rotation shaft X becomes the P ₁ line. The position varies from the range of P ₂ to.

Therefore, the bearing shaft on either side of the shaft must be installed to correspond to the physical stretching change of the metal shaft. If the bearing bearing parts of both ends of the shaft are mechanically fixed, the bearing bearing parts are damaged because they do not correspond to the contraction and extension of the rotating shaft, or the shaft has a problem that the shaft length is curved in a straight line. Because the shaft is irreversible, once the shaft is deformed, it is not restored to its original state regardless of temperature change.

In order to cope with the expansion and contraction action of the shaft, as shown in Fig. 5, a conventional bearing assembly B composed of an inner race a, a ball b and an outer race c is formed of a shaft X. The housing (H) of the exterior which is attached to the subtracting part (e) of one end and the bearing assembly (B) is fixed to the frame (f) by the fastening bolt (v). Adhesion is possible to vary the position by flowing from side to side within. Therefore, as the shaft X expands and contracts, the entire bearing assembly B flows in the housing H.

However, the housing of the bearing is composed of a means for fixing the bearing assembly to the frame. When the upper body (cover) of the housing is fastened by bolts to the lower part of the housing fixed to the frame, the bearing and the housing are integrally formed. It fits and becomes unable to cope with the expansion and contraction action of the shaft by the long time operation. In addition, when the upper part of the housing is loosely fastened, the bolt is gradually relaxed by the rotational vibration of the shaft, such that the bearing assembly may be separated from the housing along with the rotating shaft.

The present invention is easy to install the shafts of various mechanical mechanisms to the inner race of the bearing in order to solve these problems of the prior art, and retains the original lubrication support function while structurally responding to the shrinkage and stretching action in the bearing itself. A new self-aligning free-form split bearing was developed.

An object of the present invention is to divide the inner race and the outer race of the bearing in a split type so that the shaft of the various mechanical mechanisms can be easily mounted on the bearing, and the physical expansion and extension of the shaft according to the rise in temperature during operation of the machine The present invention provides a self-aligning free-form split bearing capable of supporting the lubrication support of the shaft.

Another object of the present invention is to provide an inner race and an outer race of a bearing in order to be easily fitted to the shaft as a split bearing and to retain the lubrication support function of the shaft while responding to the expansion and contraction of the shaft. It is to provide a self-aligning free-form split bearing which allows the inner race to flow from side to side due to the expansion of the shaft with respect to the outer race with several rollers arranged in the circumferential raceway of the race.

Another object of the present invention is to be commonly mounted on both ends of the shaft, even if the housing is firmly fastened to the expansion and contraction of the shaft to correspond to each bearing assembly of the shaft can improve the mechanical safety for shaft rotation more It is to provide self-aligning free-form split bearing.

According to the present invention, a plurality of rollers are disposed between the outer circumference of the inner race of the split bearing and the inner circumference of the outer race. It can be attached to the frame, and the outer ring of the roller arranged on the outer raceway of the inner race can be attached to the frame by the housing by annular coupling of the divided outer race.

The roller is formed in a cross section of an elliptic curve in which the center part thereof is convexly expanded compared to both ends thereof, and the outer circumference of the inner race and the inner circumference of the outer race each have a cross section thereof. It is formed to be concaved into a more gentle curved cross section than the curved cross section of the roller, and the bulging part of the roller is rotated by a point or preemptive point on the raceway surface so that the bearing is automatically cautious. It is intended.

The gap between the left and right annular flanges, which serve as the assembly members of the inner races projecting on both edges of the outer raceway of the inner races, is formed to have a width larger than the length of the rollers. According to the expansion and contraction of the shaft, the axial center flow (軸心 遊動) is possible to be configured.

In the present invention, when the roller of the bearing is a flat roller without change in inner diameter, the outer circumference of the inner race and the inner circumference of the outer race are formed in a planar annular shape, but the distance between the left and right flanges of the inner race is a roller. It is formed with a gap larger than the length of the inner race with the roller between the outer race in the gap between the left and right in the gap between the left and right in accordance with the expansion and contraction of the shaft is the same as the above-described bearing.

The bearing of the present invention divides the inner race and is fastened by a fastening means such as a bolt to the engaging portion of the inner race so as to respectively face the insertion hole of the inner race divided into the insertion portions of the insert portions on both end sides of the shaft. The race is firmly fitted to the insertion part of the shaft, several rollers are arranged on the outer raceway of the inner race, the divided outer races are combined, and the housing is fastened to the outside so as to be firmly fixed to the body.

Since the bearing of the present invention is divided into the inner race and the outer race, the bearing can be easily mounted on the frame of a heavy machine tool, which can be installed in the frame, and the old bearing can be easily replaced during use. .

The inner race rotates the inner circumference of the outer race by the rotation of the shaft with the roller interposed therebetween. At this time, the bulge of the roller is rotated in contact with the outer circumference of the curved section of the inner race and the inner circumference of the outer race. Because the contact surface rotates the curved surface of the roller, the bearing expands automatically due to the inclined surface or the curved surface of the roller, and there is no trembling when the shaft rotates.

In addition, even if the outer race of the bearing is fixed firmly to the frame by the housing, when the shaft expands and contracts according to the temperature, the inner race of the bearing interleaved with the insertion part of the bearing is placed between the rollers according to the expansion and contraction of the shaft. The shaft center flows from side to side with respect to the outer race so as to effectively cope with the expansion and contraction of the shaft, and the lubrication rotation function of the simultaneous shaft that securely supports the shaft is maintained.

In addition, the inner race of the bearing can move axially from side to side with the outer race as the shaft expands and contracts. It is possible to further improve the mechanical stability.

In addition, since the bearing of the present invention is commonly used at both ends of the shaft, the expansion and contraction of the shaft is performed at both ends of the shaft. The axial flow range becomes narrower. Therefore, even in the case of a large elongated shaft having a very high elasticity ratio, it is possible to effectively cope with the expansion and contraction of the shaft, thereby maintaining the safe rotational conditions of the shaft.

Since the bearing of the present invention is divided into the inner race and the outer race, the bearing can be easily fitted to the shaft of the medium-mechanical mechanism and installed in the frame, and the old bearing can be easily replaced.

Compared to the roller with the expanded elliptic curve cross section, the outer circumference of the inner race and the inner race of the outer race are concave with looser curvature. As the point or line contact is rotated, self-aligning of the bearing is made so that there is no tremor during rotation of the shaft.

 In addition, since the gap between the left and right ends of the inner race of the bearing is larger than the length of the roller, the gap is formed between the roller and the flange, so that the inner race can move axially to the left and right with respect to the outer race. Therefore, it can effectively support the expansion and contraction of the shaft to lubricate the shaft more safely, and there are various effects that can be used more safely and conveniently for the bearing of various machines and the machine bearing of the long shaft.

1 is a side view cut away a part of the split bearing of the present invention;
Figure 2 is a longitudinal cross-sectional view of Figure 1
Figure 3 is a schematic diagram of the expansion and contraction relationship of the shaft
Figure 4 is a cross-sectional view showing the use of the bearing of the present invention
Figure 4a is an explanatory view of the operation of the axial flow of the present invention
Figure 5 is a cross-sectional view showing the use of the conventional bearing

As shown in Fig. 1 and Fig. 2, the inner race 2 and the outer race 3 of the split bearing 1 are divided to form the outer circumferential trajectory 2t and the outer race 3 of the inner race 2, respectively. A plurality of rollers 4 are disposed between the inner circumferential tracks 3t of the grooves, in the engaging holes 2h of the engaging portions 2b provided at both ends of the flange 2f of each divided inner race 2. By fastening the two divided inner races 2 with fastening means 2c such as bolts, and annularly engaging the insertion portions xa of the shaft X to the insertion holes 2a of the inner races 2. The housing H is provided to the frame F. As shown in FIG.

The roller 4 is symmetrically formed in a cross section of an elliptic curve in which the central portion of the main surface 4s is convexly expanded relative to both ends thereof, and the outer raceway 2t of the inner race 2 and the outer race ( The inner circumferential track 3t of 3) is formed such that each raceway surface 2s and 3s is recessed into a cross section of a gentle curve having a greater arc degree than the curve of the main surface 4s of the roller 4. The bulging part 4c of the said roller 4 is rotated by the point or preoccupation point to the said track surface 2s (3s), and a bearing is made to be careful automatically.

The distance w of the left and right annular flanges 2f and 2f serving as the assembly member of the inner race projecting on both edges of the outer circumferential track 2t of the semi-cylindrical inner race 2 is the length of the roller 4 ( It is formed with a width larger than l), and the clearance gap c is provided in the outer periphery raceway surface 2t of the both ends of the roller 4. As shown in FIG. Therefore, the inner race 2 with the roller 4 interposed therebetween according to the expansion and contraction action of the shaft in the clearance gap c of the interval w between the left and right annular flanges 2f and 2f with respect to the outer race 3. Axial flow (로 心 遊動) can be configured from side to side.

The bearing of the present invention configured as described above engages the inner race 2 divided in the insertion part xa of both ends of the shaft X as shown in FIG. 4 and fastens like a bolt to the engaging hole 2h of the engaging part 2b. The two inner races 2 annularly coupled by means 2c are fastened to fit the insertion portions xa of the shaft X to the insertion holes 2a of the inner race 2, and the inner races are fitted. A plurality of rollers 4 are annularly arranged on the outer periphery of (2), and then the outer races 3 separated on the outside are joined to each other and the bearings 1 are firmly fixed to the frame F by the housing H. To be installed.

When the shaft X is rotated, the inner race 2 of the bearing 1 fitted to the insertion portion xa of the shaft X is rotated, and thus the outer circumferential track 2t and the outer race ( The roller 4 is rotated while the load of the shaft is applied along the inner circumferential track 3t of 3), and the lubrication rotation of the shaft X is maintained.

At this time, the expanded portion 4c of the roller 4 is curvedly recessed in the raceway surface 2s of the outer raceway 2t of the inner race 2 and curvedly recessed in the inner raceway 3t of the outer race 3. Because the roller 4 rotates in the point or line contact with the track surface 3s, the bulging part 4c of the roller 4 has the property of climbing on the inclined surface or the curved surface, so that the bearing is automatically watched, and the shaking during rotation of the shaft none.

In addition, as shown in Figure 4, the outer race 3 of the bearing (1) is mechanically fixed to the frame (F) by the housing (H), at which time the shaft (X) occurs at the ambient temperature or the machine itself When the extension part xa of the shaft X is fitted to the insertion hole 2a of the inner race 2 of the bearing 1 when it expands and contracts according to the temperature change by the inferior inferiority of the shaft X, According to the stretching action, the inner race 2 flows to the left and right with respect to the outer race 3 with the shaft 4 and the roller 4 interposed therebetween, effectively coping with the stretching action of the shaft.

In other words, as shown in Fig. 4A, the inner portion k1 of the outer race 3 of the bearing 1 is fixed to the reference line p ₀ position by the housing H and is inserted into the insertion portion of the shaft X. When the center portion k2 of the race 2 is also located at the reference line p ₀ , the expanded portion 4c of the roller 4 has a center portion k2 in which the raceway surface 2s of the inner race 2 is curved. ) And the raceway surface 3s of the outer race 3 come into contact with the center line k1 concavely curved to coincide with the reference line p ₀ .

As indicated by the dotted line in FIG. 4A, if the length of the shaft X is extended to the right side of the drawing by, for example, d, the inner race 2 of the bearing 1 is also moved to the right side together with the shaft X. The center portion k2 of the raceway surface 2s of the inner race 2 located at the reference line p ₀ is moved to the right by d. Therefore, an outer race fixed with the roller 4 of the bulge (4c) is moved heart (k2) of the raceway surface (2s) of the inner race (2) in contact, to the baseline (p ₀₎ by the housing (H) ( The center part k1 of the track surface 3s of 3) is shifted left and right. The roller 4 is inclined in a horizontal state because the contact point of the expanded portion 4c of the roller 4 is displaced by the left and right displacement of the center portions k2 and k1 of the raceway surfaces 2s and 3s.

Compared to the degree of curvature of the surface of the roller 4, the arc of the recessed curvature of the raceway surface 2s of the inner race 2 and the raceway surface 3s of the outer race 3 is smoother and smoother. 4) The self-aligning function of the simultaneous bearing is maintained so that the space 4c of the roller 4 is inclined with the displacement of the roller 4 so that the inner race 2 can flow. Will be maintained.

When the length of the shaft is shortened as the shaft is contracted, the inner race can be flowed in a reverse action in which the length is extended by the expansion.

Therefore, the bearing of the embodiment of the present invention has a function corresponding to the self-alignment and expansion and contraction of the shaft and the function to safely support the lubrication rotation of the shaft to be used more safely and conveniently as a bearing of various shafts than the conventional bearings. Can be.

In the embodiment of the present invention has been described with respect to the roller bearing the center portion is expanded, even in the case of the flat roller, the action corresponding to the stretching action of the shaft is the same.

1: bearing
2: inner race, 2a: insertion hole, 2b: coupling part, 2h: coupling hole, 2t: outer circumference track,
2s: track surface, 2f: flange, 3: outer race, 3t: inner track,
3s: orbital surface, 4: roller, 4c: bulge

Claims (4)

delete delete The main surface (2t) between the outer raceway 2t in which the raceway surface 2s of the inner race 2 of the split bearing 1 is curved, and the inner raceway 3t in which the raceway surface 3s of the outer race 3 is curved ( In the case where the many roller 4 in which the bulging part 4c in which the center part of 4s) was convex was formed was arrange | positioned,
The distance w of the annular flange 2f protruding from both edges of the outer raceway 2t of the inner race 2 is formed with the clearance c larger than the length l of the roller 4, A self-aligning free-form split bearing characterized in that the inner race (2) is configured to enable axial center flow in response to expansion and contraction.
The curvature of the recessed raceway surface 2s of the inner race 2 and the recessed raceway surface 3s of the outer race 3 according to claim 3, as compared with the curvature of the main surface 4s of the roller 4. A self-aligning free-form split bearing characterized in that the inner race (2) in contact with the bulge (4c) of the roller (4) is relatively large and configured to allow left and right flow.

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