JP2857220B2 - Rolling roller bearing - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a rolling roller bearing which rotates in only one direction.

2. Description of the Related Art Rolling bearings generally include cylindrical roller bearings, tapered roller bearings and self-aligning roller bearings.

In tapered roller bearings, the rollers linearly contact the inner and outer rings, and all radial loads are vertical loads acting on the contact parts.On the other hand, in tapered roller bearings and spherical roller bearings, the radial loads are inclined. The vertical load and the load parallel to the direction of the inclined plane are applied at right angles to each other.However, a thrust load is applied to prevent axial displacement between the inner and outer rings. It acts as an acting contact surface pressure. In addition, a vertical load acting on the contact surface between the inner and outer rings causes a force to push the rollers out of the track from the small end to the large end, so it is necessary to provide a guide flange on the large end to prevent the rollers from jumping out. Occurs. However, since sliding contact occurs between the large end surface of the tapered roller and the guide flange, the PV value due to the sliding friction is a great limitation on the load-loading capacity of the tapered roller bearing.

Problems to be Solved by the Invention Rolling roller bearings rotate in both forward and reverse directions and are often used for such applications. However, depending on the machine in which the bearing is incorporated, there are many cases where the bearing rotates only in one direction.

The present invention relates to a rolling roller bearing used in such an application, which has a larger load capacity than a conventional cylindrical / tapered roller bearing, and which does not cause a large sliding friction at a large end portion of the roller as in a tapered roller bearing. It is an object of the present invention to provide a rolling bearing having improved performance, high efficiency, suitable for high rotation, and free from seizure.

Means for Solving the Problems In order to solve the above problems, the present invention has a structure including an inner ring, an outer ring, and an intermediate rotating body, and a biasing means, and the inner ring is a single leaf around one axis. An inner raceway surface forming a hyperboloid of revolution; the outer race having an outer raceway surface forming a single-plane hyperboloid of rotation about the one axis; the inner raceway surface and the outer raceway surface being opposed to each other, and from one end to the other. A track whose radius increases toward the end side is formed, and the intermediate rotating body has a cylindrical surface or a conical rolling surface, and the central axis of the intermediate rotating body in the track is at a predetermined angle from a cross section including the axis. A plurality of the intermediate races are arranged in the circumferential direction of the raceway so as to be inclined, and the surface of the intermediate rotation body linearly contacts the inner raceway surface and the outer raceway surface, and the inner ring or the outer race is the intermediate rotation body. Along the inner raceway in the uniaxial direction An annular portion that rotates only in a certain direction such that it rolls in a direction in which the track radius is smaller, and stops the axial movement of the intermediate rotating body when the inner ring or the outer ring rotates in the certain direction. The structure is disposed so as to face the one axial direction, and the biasing means is provided between the inner ring or the outer ring which is provided so as to face the one axial direction,
The inner ring or the outer ring opposing each other is urged in a direction to reduce the interval of the track, and the inner ring or the outer ring opposing each other in the uniaxial direction, which are not urged by the urging means, It is fixed so as not to move in the axial direction.

Action Since both the inner raceway surface and the outer raceway surface are single-leaf hyperboloids, the trajectory formed by them increases in radius from one end to the other end. And, in this, the intermediate rotating body is provided inclined with respect to the axial section, so that when the inner ring or the outer ring is rotated when used as a bearing, the intermediate rotating body is guided by both raceway surfaces to maintain line contact. While rolling over it, he tries to move in the axial direction. However, in the inner raceway surface and the outer raceway surface, the directions in which the intermediate rotating body tends to advance in the axial direction are opposite to each other, and as a result, the inner ring and the outer ring are separated from each other in the axial direction via the intermediate rotating body. Receive.

In this case, since the inner ring or the outer ring rotates only in a fixed direction such that the intermediate rotating body advances on the inner raceway surface in the direction with the smaller track radius, the separating force moves the inner ring in the direction with the larger track radius to move the outer ring. The force acts to move the track in the direction of a smaller radius of the track, and an effect of always increasing the track interval is generated between the inner and outer wheels.

On the other hand, the components including the inner and outer races and the intermediate rotating body are disposed to face each other in the axial direction, and one set of inner races or outer races facing each other in the axial direction is fixed in the axial direction and the other set is formed. Since the biasing means urges the raceway in the direction of narrowing the track interval, the inner and outer wheels facing each other in the radial direction do not separate from each other due to the separating force, and the inner and outer wheels are pressed from the opposite direction while receiving the separating force. Under the influence, it rotates while floating from the intermediate rotating body.

As a reaction in which the inner and outer rings receive the separating force, the intermediate rotating body receives forces in the axial direction opposite to each other from the inner and outer rings. And if there is a difference in this force,
The intermediate rotator will move in the axial direction. When the intermediate rotator has a conical shape, the intermediate rotator also receives a force pushed from the small end to the large end, and moves in one of the axial directions depending on the balance with the separating force. The annular portion provided on the inner ring or the outer ring functions to stop the intermediate rotator from moving at a predetermined position and prevent the intermediate rotator from slipping off the track.

Next, the magnitude of the separating force generated on the contact line between the intermediate rotating body and the inner and outer raceway surfaces differs depending on the state of each contact. That is, the intermediate rotating body contacts the inner raceway surface with the convex portions, but the outer raceway surface comes into contact with the convex portion and the concave portion, so that the contact surface pressure generated when a radial load is applied is: The inner raceway side becomes larger, and the separating force becomes larger on the inner raceway side. As a result, when the intermediate rotating body has a cylindrical shape, the difference in the separating force causes the intermediate rotating body to advance in the axial direction and hit the annular portion and stop, and this difference in force is generated between the intermediate rotating body and the annular portion. It will act as contact surface pressure. However, this difference in force is not so great that friction at the contact does not matter.

On the other hand, when the intermediate rotating body has a conical shape, the intermediate rotating body receives the pushing force due to the pressure of the contact portion as described above, but the contact pressure itself is reduced by the separating force and the difference in the separating force is increased. Since it acts in the opposite direction to the force, no large contact surface pressure is generated between the intermediate rotating body and the annular portion.

FIG. 1 is a sectional view showing an example of a rolling roller bearing according to the present invention, FIG. 2 is a perspective view of a part thereof, and FIG. 3 is a perspective view of an intermediate rotating body part thereof.

First, the structure of the present rolling roller bearing will be described with reference to these drawings.

At least one set of components 20, 20 'including the inner rings 1, 1' and the outer rings 2, 2 'including rollers 3, 3' as intermediate rotating members is provided so as to face each other to constitute the present bearing. Construct 2
Since 0 and 20 'have the same structure, the structure 20 on one side
Will be described.

The inner race 1 is mounted on the shaft 4 by, for example, a key 5 and forms a raceway 8 with an inner raceway surface 1a and an outer raceway surface 2a between the inner race 1 and an outer race 2 provided opposite thereto.

The roller 3 as an example of the intermediate rotating body has a cylindrical shape,
As shown in FIG. 3, a large number are arranged in the track 8 at an angle β, for example, about 15 °, with respect to a cross section including the central axis 6 of the inner ring 1 which is one axis.

In this embodiment, a preload spring 7 as an urging means is provided between the inner rings 1, 1 'which are disposed opposite to each other, and applies a preload between the inner rings 1, 1'. The direction of the preload is a direction in which the interval between the tracks 8 is narrowed, that is, a direction in which the distance between the inner rings 1 and 1 'is increased.

Further, the inner ring 1 is provided with a collar 9 as an annular portion for stopping the movement of the roller 3 in the axial direction. This is to stop the advance when the inner ring 1 rotates and the roller 3 rotates and advances in the direction of the central axis 6. In addition, it is also possible to provide the collar 9 on the outer ring 2 side.

In FIG. 3, the rollers 3 are arranged on the inner ring 1 at an angle β from the cross section including the central axis 6, and the positions between the rollers are held by retainers 10 so as not to contact each other. . In this way, the adjacent rollers that rotate in the same direction do not collide with each other at tangential velocities in opposite directions, and the rotation and revolution of the roller 3 become smooth.

In the rolling roller bearing according to the present embodiment, the shaft 4 is always in a fixed direction.
Direction). The shaft 4 moves the inner ring 1 in the same direction (A
Direction, the roller 3 is guided in contact with the inner ring raceway surface 1a while linearly contacting the inner ring raceway surface 1a. ,
Go left in the figure.

On the other hand, if the roller 3 rotates in the B direction shown in the drawing, the roller 3 also rotates while maintaining line contact with the outer raceway surface 2a, and tries to move rightward in the figure.

FIG. 4 is a diagram for explaining the relationship between the forces received by the inner and outer wheels due to the movement of the rollers 3.

The roller 3 and the inner and outer raceway surfaces 1a and 2a make line contact (actually, they come into linear or planar contact with a fixed width), but they are part of it for simplicity of explanation. Consider contact points A and B. The roller 3 has an angle β with respect to the central axis 6 section.
As the roller 3 is rotated, the inner and outer races rotate when the roller 3 is rotated because the direction S of the rotation is inclined β with respect to the direction T of the track cross section perpendicular to the center axis 6. As shown in the drawing, the components 3 and To of the roller 3 in the revolving direction and the components Ri and Ro of the roller 3 in the axial direction are received.

Due to the generation of the component forces Ri and Ro, the inner ring 1 and the outer ring 2
In this embodiment, since the outer ring 2 is fixed by receiving forces that are pulled away from each other in the direction of the central axis 6 via the roller 3, the inner ring 1 is moved rightward in FIG. It will move in the direction to increase the interval.

Such a force acting on the inner and outer rings balances the urging force of the preload spring 7 to generate an effect of lifting the inner and outer rings against the roller 3, thereby reducing the rolling contact surface pressure, smearing and meshing during overload. And prevent accidents such as quenching.

As for the contact of the roller 3 with the inner and outer rings, as shown in FIG. 5, the contact between the roller 3 and the outer ring 2 is the contact between the convex portion of the roller 3 and the concave portion of the outer ring raceway surface 2a. Since the convex portions come into contact with the inner ring raceway surface 1a, the maximum contact surface pressure Pi on the inner ring 1 side becomes larger than the maximum contact surface pressure Po on the outer ring 2 side. Therefore, at the contact portion between the roller 3 and the inner and outer rings, local deformation is larger on the inner ring 1 side than on the outer ring 2 side. As a result, when the same vertical force N acts on the inner and outer wheels, and the rollers 3 rotate, the force Ri for moving the inner wheels 1 by the rollers 3 becomes greater than the force Ro for moving the outer wheels 2.

As a reaction of such component forces Ri and Ro, the roller 3 has the same magnitude as Ri and Ro from the inner and outer rings, and the forces −Ri and −Ro in the opposite directions.
As a result, the roller 3 is guided on the inner ring raceway surface 1a side and advances leftward in the direction of the central axis 6 in FIGS. In order to stop such movement of the roller 3, the collar 9 is provided as described above.

In this case, the sliding contact between the flange 9 and the end face of the roller 3 occurs at the time of rotation and revolution of the roller 3, but the pressure contact force during this period is (Ri-Ro) and does not become a very large value. This sliding friction is not a problem for us.

As a result, in the present bearing, problems such as seizure due to excess PV value of the guide flange at high speed rotation and occurrence of various accidents due to poor lubrication, which are seen in the conventional conical roller bearing, are solved. Furthermore, since the sliding friction loss is small and high-speed rotation is possible, the mechanical loss of the bearing is small and the bearing efficiency is greatly improved.

 FIG. 6 shows another embodiment.

In the rolling bearing of this embodiment, the inner ring 1 is fixed to the shaft 4 so as not to move in the axial direction, the outer ring 2 is movable in the axial direction, and a preload spring 7 is provided between the outer rings 2, 2 '. ing.

Therefore, in this bearing, when the shaft 4 is rotated in one direction,
The rollers 3, 3 'rotate to advance the outer races 2, 2' in a direction approaching each other, which is a direction for increasing the track interval, and the inner and outer races 1, 2 '
1 'and 2, 2' float from the rollers 3, 3 ', and the contact surface pressure therebetween is reduced. In addition, since the mechanism and functions of this bearing are basically the same as those shown in FIG.
Detailed description is omitted.

Next, the shape of the inner and outer raceway surfaces 1a and 2a required for the roller 3 to make line contact with the inner race 1 and the outer race 2 will be described.

7 to 9 are explanatory diagrams for obtaining these shapes, and show a case where the roller 3 is a cylindrical roller.

First, FIG. 7 shows the roller 3 in the XYZ coordinates,
FIG. 9 is a perspective view showing a state where the center axis 3a is located at a distance F from the origin O on the Y axis, passes through the Y axis, is parallel to the XZ plane, and is inclined at an angle β with respect to the XY plane. in this case,
The X axis indicates a common central axis 6 of the inner and outer rings 1 and 2. And
The cross section 3b of the roller 3 is a cross section obtained by cutting the roller 3 at a position at an arbitrary distance x on the X axis and a plane parallel to the YZ plane, and points Uc and U '
c is the X-axis and X-axis, respectively, from the center Pc of the roller 3 on that surface.
-The intersection of the perpendicular drawn down on the Z plane with the X axis and the XY plane. In this case, a line 3a 'passing through the origin O and U'c is a line obtained by projecting the central axis 3a of the roller onto the XZ plane, and forms an angle β with the X-ray. As is clear from this figure, ▲ ▼ = x tanβ ▲ ▼ = F. Therefore, assuming that the distance from the center axis 6 to the center Pc of the roller 3 on the X axis is ▲ ▼ = yc, yc ² = F ² + (X tanβ) ² Therefore, yc ² / F ² −x ² / (F / tan β) ² = 1 (1) Since the equation (1) is an equation showing a hyperbola, the axis of the roller 3, that is, the inner and outer rings 1 The center line of the axial path formed by 2 and 2 is hyperbolic with respect to the center axis 6.

FIG. 8 is a view for explaining a state in which the inner and outer races 1 and 2 come into contact with the rollers 3 arranged as described above.

Let Q be the intersection of the X axis with a plane passing through the center point Pc of the roller 3 and perpendicular to the axis 3a of the roller 3. Considering the spheres Si and So inscribing and circumscribing the roller 3 around the point Q (the sphere So circumscribing in FIG. 8), the contact points Pi and Po between the roller 3 and the spheres Si and So are perpendicular to ▼ It will be on top, Pc
The positions are separated from the point by the radius r of the roller 3.
Therefore, if ▼ = R, the radii of the spheres Si and So are R−r and R + r, respectively.

Let Ui and Uo be the intersections between the plane passing through points Pi and Po and the plane parallel to the YZ plane and the X axis, respectively (see FIG. 9).
▼ and ▲ ▼ indicate the distance from the point Pi and the point Po to the X-axis, respectively, and the distance ▲ ▼ and ▲ from the origin O
▼ indicates the coordinates of the points Pi and Po on the X-axis, respectively. Therefore, ▲ ▼ = xi, ▲ ▼ = xo,
If ▲ ▼ = yi and ▲ ▼ = yo, the relationship between xi and yi and xo and yo is expressed by the formulas F (xi, yi) and F (xo, yo) representing the curved surface shapes of the raceway surfaces 1a and 2a of the inner and outer rings, respectively. It becomes an expression.

FIG. 9 is an enlarged view of a related portion for obtaining this relationship.

▼ indicating R is perpendicular to axis 3a and point U ′
Since c is the point at which the perpendicular from the point Pc to the XZ plane intersects the same plane, ▲ is perpendicular to the axis 3a '. Therefore, ▲ ▼ = (x / cosβ) / cosβ = x / cos ² β R ² = F ² + ｛(x / cos ² β) sin β｝ ² = F ² + x ² tan ² β / cos ² β Then ∠QPcUc = Φ, ΔQPcUc is a right triangle, so Becomes On the other hand, since ▲ ▼ = ▲ ▼ = r and ΔQPiUi and ΔQPoUo are both similar to ΔQPcUc, Becomes Then, from these equations, the relational expression F (xi, yi),
F (xo, yo) is Becomes These formulas represent the curved surface shapes of the inner and outer raceway surfaces 1a and 2a, but cannot exhibit characteristics higher than quadratic curved surfaces. Where (xi-x), (yi-y) and (xo-x)
When the respective ratios of (yo-yc) and (yo-yc) are obtained, from equations (2) to (5), And the relationship between x and yc is hyperbolic from equation (1),
And, since tan ² β is a constant in the above equation, the relationship between xi and yi and the relationship between xo and yo are hyperbolic, and therefore the inner and outer raceway surfaces
1a and 2a are single-leaf hyperboloids around a common central axis 6.

For example, the inner and outer raceways are respectively hyperbolic formulas yi ² / ai ² −xi ² / bi ² = 1 yo ² / ao ² −xo ² / bo ² = 1, F = 9, r = 1.5, β = 15 ° When actually calculated as, the values of ai, bi, ao, bo are about 7.5 and 30, respectively.
7, 10.5, and 36.2, and the inner and outer raceway surfaces are given as a single leaf rotational hyperbola.

Next, a case where the intermediate rotating body has a conical shape will be described.

FIG. 10 is a view corresponding to FIG. 1, and the rolling roller bearing of FIG. 10 is different from that of FIG. 1 only in that the rollers 3, 3 ′ are not cylindrical but conical. It is.

When the conical rollers are used, the rolling performance is further improved. On the other hand, in the case of the tapered roller bearing, sliding friction on the large end side of the roller generally becomes a problem. However, in the rolling roller bearing of the present invention, this point is improved.

 FIG. 11 is a diagram for explaining this point.

As described above, the rollers 3, 3 'are axially component-R from the inner and outer rings.
i, −Ro, and Ri> Ro, so that the roller 3 moves to the axially small end side (Ri′−R) as shown in the figure.
o '). Since the roller 3 has a conical shape,
As shown in the drawing, the roller 3 receives an axial component force u which is pushed from the small end side to the large end side by the normal force N acting on the contact surface.

Thus, the component force (Ri'-Ro ') acting on the roller 3 and u
The roller 3 moves in either direction depending on the magnitude of the above, and an annular portion for stopping the movement in the moving direction is provided on the inner ring 1 or the outer ring 2. In the bearing of the embodiment shown in FIG. 10, the collar 9 is provided on the inner ring 1 on the small end side of the roller 3 on the assumption that (Ri'-Ro ')> u.

Thus, according to the bearing using the tapered rollers of the present invention,
The pulling force u acting on the large end side of the roller 3 in the conventional tapered roller bearing is greatly reduced, and it is only necessary to provide an auxiliary flange on the large end side or the small end side of the roller 3, and the sliding friction is reduced. Will not limit the load carrying capacity.

In the case of tapered rollers, the shape of the raceway surfaces of the inner and outer races is a straight line with a slanted generatrix of the tapered rollers. Shape.

Although the bearing in FIG. 10 has a structure corresponding to the bearing in FIG. 1, it may have a structure corresponding to the bearing in FIG.

In the above embodiment, the case where the shaft 4 rotates is described. However, the shaft 4 and the inner ring 1 do not rotate and the boss side (not shown) is used.
Of course, it can also be used as a bearing on which the outer ring 2 rotates.

Further, in the above description, the intermediate rotating body has a cylindrical shape or a conical shape. However, the intermediate rotating body may be shaped like a drum or a drum.

When the surface of the roller is formed into a drum shape in which a part of an ellipse is rotated around an outer axis, the inner ring is formed in a cylindrical shape, and the outer ring is formed by a curved surface obtained by combining a spheroidal surface and a hyperboloid of revolution.
When the surface of the roller is formed into a drum shape in which a part of an ellipse is rotated about its central axis, the inner ring is a composite curved surface of a spheroid and a hyperboloid, and the outer ring is a cylindrical shape.

Effects As described above, according to the present invention, by disposing the intermediate rotating body at an inclination in the track, separating the inner and outer races, floating the inner and outer rings from the intermediate rotating body, and making the axial movement of the intermediate rotating body uniform. In addition, it is possible to improve bearing load capacity and rolling performance, prevent the occurrence of various accidents due to seizure and poor lubrication without large sliding friction, and facilitate high-speed rotation and improve bearing efficiency.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a rolling roller bearing according to an embodiment, FIG. 2 is a perspective view of a main part thereof, FIG. 3 is a perspective view showing an arrangement of rollers, and FIGS. Fig. 6, Fig. 6 is a cross-sectional view showing another embodiment, Figs. 7 to 9 are explanatory views for obtaining a track shape, Fig. 10 is a cross-sectional view showing still another embodiment, Fig. 11 is It is explanatory drawing of the force which acts on a roller. 1, 1 '... inner ring 1a, 1a' ... inner ring raceway surface (inner raceway surface) 2, 2 '... outer ring 2a, 2a' ... outer ring raceway surface (outer raceway surface) 3, 3 '... roller ( Intermediate rotating body) 6 Central axis (1 axis) 7 Preload spring (biasing means) 8, 8 'Track (annular section) 9, 9' ... Flange (annular section) 20, 20 ' … Constitution

Claims (1)

(57) [Claims] An inner race having an inner raceway that forms a single-plane hyperboloid of revolution around a single axis; and a biasing means, the inner race having an inner raceway. Has an outer raceway surface that forms a single-plane rotational hyperbola around the one axis, and the inner raceway surface and the outer raceway surface are opposed to each other and form a trajectory whose radius increases from one end to the other end. The intermediate rotating body has a cylindrical surface or a conical rolling surface, and the center axis of the intermediate rotating body is inclined at a predetermined angle from a cross section including the axis in the track, and a plurality of the rotating shafts extend in a circumferential direction of the track. The surface of the intermediate rotating body is linearly contacted with the inner raceway surface and the outer raceway surface, and the inner ring or the outer ring moves the intermediate rotating body along the inner raceway surface in the uniaxial direction. Rolling in the direction where the orbital radius is smaller at The inner ring or the outer ring rotates only in a fixed direction, and the inner ring or the outer ring includes an annular portion that stops and stops the movement of the intermediate rotating body in the axial direction when rotating in the fixed direction. The urging means is provided between the inner races or the outer races arranged opposite to each other in the one axial direction, and the inner races or the outer races facing each other are arranged on the raceway. The inner ring or the outer rings which are opposed to each other in the one axial direction and are not biased by the biasing means are fixed so as not to move in the axial direction. Rolling roller bearings.