JPS6311533B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an elastic bearing. Among the conventional bearings, radial ball bearings, angular ball bearings, self-aligning ball bearings, roller bearings, cylindrical roller bearings,
In both conical roller bearings and needle bearings, each element of the bearing is made of a rigid body, and the bearing as a whole is also a rigid body.

Therefore, when used in a machine part, changes in the temperature of the machine may create a very large gap between the respective elements of the bearing, or a very large buffer between the elements may occur, impairing the accuracy of the machine. This may cause the machine to deteriorate or even damage the entire machine. In other words, when the temperature of the mechanical parts becomes higher than the bearing part, the outer ring part of the bearing expands, resulting in an excessive gap between the outer ring and the inner ring, which reduces the precision of the machine and causes balls and rollers to break out. This causes a sliding phenomenon, and the entire bearing suffers from seizing failure.

Conversely, if the temperature of the mechanical part is lower than that of the bearing part, the mechanical part and the outer ring will shrink due to heat, so the clearance between the inner and outer rings will become too small, and the steel balls will act as a buffer between the inner and outer rings. This causes the surface pressure to become excessive, resulting in poor rotation or damage to the bearing, which can lead to an accident.

Another problem is when an external force is applied shockingly to a bearing incorporated in a machine.

In this case, of course, in a rigid bearing, since the impact load is directly applied to the outer ring, rollers, and inner ring, the rigid bearing may be damaged.

Furthermore, the effects of the aforementioned expansion and an impactful external force may act at the same time, and in this case, the external force conditions acting on the bearing become even more severe, which often leads to accidents.

As mentioned above, conventional rigid bearings suffer from thermal expansion in high-temperature atmospheres, thermal contraction in low-temperature atmospheres, impact loads due to external impact forces, or when a combination of these acts on the bearings. The reality is that the lifespan of bearings is significantly reduced due to decreases in machine accuracy, abnormal bearing wear, seizure, and damage.

The present invention was made to solve these problems with bearings, and its purpose is to ensure that when a machine undergoes thermal expansion or contraction, the bearing itself elastically deforms to follow the deformation of the machine. However, the purpose is to allow the bearing to operate without degrading its function.Another purpose is that when an impactful external force is applied to the bearing part of a machine, the elastic bearing itself temporarily absorbs the impact energy. By absorbing energy, that is, through the elastic deformation of the bearing's outer shaft or inner ring and elastic rollers, the bearing is able to fully perform its functions while absorbing impact energy. be.

The present invention will be explained below based on illustrated embodiments. In the figure, 1 is a shaft, and the outer periphery of the end of the shaft 1 is rotatably supported by an elastic bearing 2 of the present invention. As shown in FIG. 1, this elastic bearing shaft 2 has an inner ring 3 fitted on the outer periphery of the shaft end, an outer ring 5 fitted inside the bearing body 4, and a large number of them arranged in a planetary pattern between the inner and outer rings. To explain this in more detail, both the inner ring 3 and the outer ring 5 are preferably formed by winding band-shaped metal plates having desired elasticity into a coil shape so as to have respective diameters. The plate-shaped side surfaces forming both the inner and outer wheels have arcuate surfaces that contact each other when wound into a coil shape, allowing the coil itself to make a predetermined displacement, and the displacement (flexibility) ), the contact surface should slide smoothly.

Although not shown, the elastic rollers 6 fitted between the inner ring 3 and the outer ring 5 and rotatably supported are made of thin strip-shaped metal plates having the same cross-sectional shape as the inner and outer rings, that is, both sides are arcuate. Either the sides are in contact with each other and the metal plates are wound into a coil, or two thin strip metal plates 6X and 6Y with trapezoidal cross sections are wound in different directions as shown in Fig. 5. Rings 6a and 6b wound in a coil shape or tapered inversely to each other as shown in FIGS. 1 and 3 are arranged alternately, that is, the ring 6a is shaped like a Soroban bead, and the inner circumference is thinner than the outer circumference. The trapezoidal rings 6b are arranged alternately on the same axis, and one roller shaft 6c is passed through each ring hole, and both ends of the shaft 6c, that is, the shaft head, are connected to a fastener 6 such as a nut.
d and are strongly pressed together to form a unit. In this case, disc springs 6e, 6e are interposed on the outside of the outermost ring 6a or 6b so as to absorb the force in the longitudinal direction of the axis of the elastic roller. At this time, desirably, the Soroban-shaped ring 6a is fitted with the outer circumferential surface of the roller shaft without any gap, and the trapezoid-shaped ring 6b is preferably fitted with a slight gap between it and the roller shaft. When the elastic rollers are formed by arranging multiple rings, this roller shaft is supported through all the rollers, but when it is formed by winding a band-shaped metal plate into a ring shape, it is not necessary to penetrate through all the rollers. do not have.

Further, a large number of elastic rollers 6 configured as described above are fitted and supported in the ring space between the inner and outer wheels so that the elastic roller axis is always kept parallel to the axes (longitudinal direction of the axes) of the inner and outer wheels. , each of the elastic rollers is rotatable so as to rotate and revolve within the ring-shaped space between the inner and outer rings. At this time, in order to ensure that the axes of the elastic rollers are all parallel to the axes of the inner and outer rings, cages 7, 7 are arranged on both sides of the elastic rollers, and elastic rollers are arranged on one side of the cage in the ring direction. Either the protrusion protruding from the end of the elastic roller is fitted into a guide hole drilled at a fixed pitch according to the diameter, or an engaging hole 6f is bored at the end surface of the elastic roller shaft as shown in Fig. 6. , a large number of pins 7a are provided on the side surface of the cage corresponding to the elastic rollers and protrude in the circumferential direction of the cage at a pitch that matches the diameter of the elastic rollers.
When the retainer 7 revolves, the elastic rollers revolve and each roller also rotates on its own axis.

The cage is fitted into the space between the inner and outer wheels, and is supported within the bearing body.

Further, the embodiment shown in Fig. 3 uses pipe-shaped inner rings 3 and outer rings 5, and the embodiment shown in Fig. 4 uses Soroban ball-shaped rings 3a and 5a for both the inner ring and outer ring, similar to the elastic rollers. ladder-shaped ring 3
An embodiment is shown in which b and 5b are arranged alternately with each other. In these embodiments, an example of which is shown in FIG. 4, disc springs are provided to absorb external forces in the axial direction applied to the inner and outer rings. As shown in the figure, the disc spring 8 may be applied only to one end of the inner and outer rings, or may be applied to both ends. This disc spring 8 can also be employed in the embodiments shown in FIGS. 1 and 3.

FIG. 6 is an explanatory diagram showing the transmission and dispersion of the external force δ in the axial direction applied to the bearing and the external force P applied from the outer peripheral direction of the shaft.

In addition, what is shown in FIG. 7 shows an embodiment in which the elastic bearing of the present invention is inserted into a roll to form a flexible roll. The roll shaft 11 supported by
A large number of them are arranged between.

In contrast to the force P that is always applied to the shaft 1, let P' be the impact load that is applied occasionally.

Assuming that the impact load P' acts on one ring 3a is P', when the impact load P' acts on the ring 3a, P' is dispersed in the thrust direction and the radial direction by the taper angle α.

Example Shock load P′ in radial direction If the taper angle of the ring is 76°, Shock load P′ _S in thrust direction is P′ _S = P′sin76°=0.97030P′ Shock load P′ _R in radial direction is P′ _R = P′cos76゜=0.24192P′ In other words, when the impact load P′ in the radial direction acts on the shaft, 97% of the load P′ _S in the thrust direction can be absorbed by the disc spring 8, so it acts on the bearing rollers. The impact load P′ _R can be made very small at 0.242P′.

Furthermore, the impact load P′ _R =0.24192P′ applied to the roller ring 6X by the outer ring 3b is
The same effect occurs between X and ring 6Y, so the impact load 0.24192P' received by ring 6Y is P'' _S
and P″ _R .

Therefore, P″ _S =0.24192P′・sin76°==0.97030×0.24192P=0.2347P′ Also, P″ _R =0.24192P′・cos76°=0.24192×0.24192P′=0.0585P′.

That is, the impact load acting on the housing can be reduced to about 0.0585 times, ie, about 1/17, of the impact load acting on the shaft.

From the above, the impact load in the structure shown in FIG. 6 can be reduced to about 1/17, and even in the case of the structure shown in FIG. 1, it can be reduced to about 1/4.

According to the present invention, when the machine undergoes thermal expansion or contraction, the bearing itself elastically deforms to follow the deformation of the machine, and the bearing can operate without deteriorating its function. When an impactful external force acts on the bearing part of a machine, the impact energy is temporarily absorbed by the elastic bearing itself, that is, due to the elastic deformation of the outer or inner ring and elastic rollers of the bearing. The function of the bearing can be fully demonstrated in a state where the impact energy is absorbed.In both cases, elastic bearings are designed to absorb energy within the elastic limit against external forces, so the external force is If it disappears, it can be restored to its original state. Of course, even while the machine is expanding or contracting, or at the moment when impact energy is applied, the elastic bearing can fully perform its function as a bearing while being elastically deformed. Furthermore, even if the roll and roll shaft are curved, the outer ring, inner ring, and rollers of this elastic bearing are elastic bodies, so they can elastically deform along the curves of the roll pipe and roll shaft, so the roll will not curve. It can also perform its function as a bearing without any damage. In addition, since this elastic bearing has a long contact surface in the axial direction, it can withstand a much larger force (radial load) than a fixed bearing. Since the external force applied to the pipe can also be applied to the shaft, it is safe from the viewpoint of the mechanical strength of the roll. It has many excellent advantages such as:

[Brief explanation of the drawing]

Fig. 1 is a sectional view of the elastic bearing of the present invention, Fig. 2 is a side view thereof, Figs. 3 and 4 are sectional views of different embodiments, Fig. 5 is an explanatory diagram of the elastic roller, and Fig. 6 7 is an explanatory diagram of the force acting on the bearing of the present invention, and FIG. 7 is a partially cutaway front view of an embodiment of a flexible roll. 1... Shaft, 2... Bearing, 3... Inner ring, 4... Bearing body, 5... Outer ring, 6... Elastic roller, 7... Cage, 8... Belleville spring, 9... Roll, 10 ... Bearing, 11 ... Roll shaft.

Claims (1)

[Claims] 1. An inner ring and an outer ring are fitted and supported on the outer periphery of the end of the shaft to be supported and the inner periphery of the bearing body, and within the ring-shaped space between the inner and outer rings, a number of rings are penetrated and supported on the roller shaft so as to be parallel to the axis. A large number of elastic rollers which are made to have elasticity are fitted and supported in a planetary manner so that they can rotate freely, and two types of rings with opposite taper angles on the sides of the inner ring, outer ring and elastic rollers are alternately arranged. A large number of elastic rollers are arranged and connected in the thrust direction by the conical slope of each ring, and the inner surface of one of the rings of these alternately arranged elastic rollers is brought into close contact with the roller shaft, and the other ring is connected to the inner surface of the ring with the roller shaft. An elastic bearing characterized in that a space is provided between the shafts to absorb axial bending, thermal deformation force, and external force in a direction perpendicular to the shaft, and to elastically deform and support the shaft.