JPH0914259A - Bearing unit and guide tool provided with bearing unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To extend the upper limit of rotating speed of a rotaing guide of a guide tool so as to be able to reduce the starting torque of the rotating guide. SOLUTION: A bearing unit B is interposed between a shaft body installed out of rotation, and a rotating guide 2. The bearing unit B is so constituted that a first rolling element row 7 with a set of rolling elements 8 arranged around the shaft body 1, and a second rolling element row 11 with a set of rolling elements 12 arranged around the first rolling element row 7 are mounted inside being piled in the radial direction of the shaft body 1. Rotational torque reducing effect obtained by combining the respective rotational torque reducing performance of both rolling element rows 7, 11 is displayed by the bearing unit B.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing unit having a function of reducing the rotational torque of a rotating body, and a guide having the bearing unit.

[0002]

2. Description of the Related Art Conventionally, a device provided with a bearing and a rotating body that rotates in a state of being coupled to the bearing, for example, a guide tool g for defining a traveling position of a traveling filamentous body such as a fiber yarn or an electric wire, As shown in FIG. 7, the inner ring 52 fixed to the shaft body 50, the outer ring 53 to which the rotation guide 55 rotating in contact with the traveling linear body is fixed, and the insertion between the inner ring 52 and the outer ring 53. A rolling bearing 51 having a plurality of rolling elements 54 arranged around the shaft body 50 is used.

[0003]

In the textile machinery field and the electric wire processing machinery field in which the above-mentioned guide tool g is used, in the textile machinery field, ultrafine fiber yarns are manufactured for the purpose of high quality, and for example, per denier. Tensile strength 4.3 to 9.
With 0 g of polyester fiber yarn, ultra-fine polyester fiber yarn composed of monofilament with a thickness of 0.1 denier is manufactured. When guiding this ultra-fine polyester fiber yarn with a guide tool g Further, even when the single fiber comes into contact with the rotation guide 55 during the traveling and receives a slight frictional resistance of 1 g or less, the single fiber is cut.

Further, when the unstretched synthetic fiber yarn comes into contact with the rotating guide 55 during traveling in the process of stretching the synthetic fiber yarn, the rotation guide 55 rotates at a rotation speed lower than the rotation speed adapted to the traveling speed of the yarn. When rotated, the synthetic fiber yarn slips and receives frictional resistance by the rotation guide 55, causing uneven stretch in the synthetic fiber yarn, and stretching due to uneven frictional resistance applied to the synthetic fiber yarn. Unevenness, uneven thickness of single fibers, breakage of single fibers, uneven dyeing, etc. occur.

On the other hand, in the field of electric wire processing machines, ultra-fine electric wires have been manufactured with the miniaturization of electric devices. Although manufactured, if an ultra-fine electric wire of this type comes into contact with the rotation guide 55 and receives frictional resistance during its running, the copper wire is broken or the insulating coating is peeled off, which is a fatal defect.

The winding speed of the synthetic fiber yarn in the spinning step has been practically increased to 6000 m / min, and it is expected that the winding speed will be further increased. In order to avoid frictional resistance, it is necessary to rotate the rotary guide 55 at a high speed at a rotation speed that follows the traveling speed of the linear body so that the linear body does not slip, and the linear body starts traveling. In order to prevent frictional resistance from being applied by the rotating guide 55, it is necessary to reduce the starting torque for starting the rotating guide 55.

An object of the present invention is to enable the rotating body to rotate at high speed and to start the rotating body with a small starting torque.

[0008]

A bearing unit according to claim 1, wherein at least two rows of rolling elements each having one set of rolling elements arranged around the shaft are stacked in a radial direction of the shaft. It has a configuration of being charged inside.

According to the first aspect of the present invention, the bearing unit is provided with the rotational torque reducing characteristic that is combined with the rotational torque reducing performance of the rolling element rows of each row, and the upper limit of the rotation speed when rotating the rotating body is expanded. The starting torque for starting the rotating body is reduced.

A guide tool according to a second aspect of the present invention is a guide tool having a shaft body which is installed so as not to rotate and a rotary guide which rotates in contact with a traveling linear body, and is provided around the shaft body. At least 2 each with one set of rolling elements arranged
It is characterized in that the rolling element rows of the rows are provided with bearing units that are stacked in the radial direction of the shaft body and are inserted inside.

According to the second aspect of the present invention, the upper limit of the rotation speed when the rotation guide rotates in contact with the traveling linear body is expanded by the rotation torque reduction effect that combines the rotation torque reduction performance of each rolling element row. The starting torque when the rotating guide is started by contacting the linear body is reduced by the rotating torque reducing effect.

The bearing unit according to the invention of claim 3 is
Between both rolling element rows adjacent to each other, an intermediate wheel circumscribing each rolling element in the inner rolling element row and inscribed in each rolling element in the outer rolling element row It is characterized by being installed in a partitioned state.

According to the third aspect of the invention, the two rolling element rows adjacent to each other are partitioned by a common intermediate wheel, and the intermediate wheel functions as an outer ring circumscribing each rolling element of the inner rolling element row and an outer rolling element. It also has the function of an inner ring inscribed in each rolling element of the moving body row.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS In the inventions of claims 1 and 2, the bearing unit has a structure in which at least two bearing elements each having a row of rolling elements are fitted and coupled to each other, and the shaft body is fixed. In this case, the member connected to the outermost bearing element rotates as a rotating body, and when the member connected to the outermost bearing element is fixed, the shaft body rotates as a rotating body.

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, a first embodiment of the present invention will be described with reference to FIGS. The guide tool G that regulates the traveling position of the filamentous body S such as a fiber yarn or an electric wire when traveling is installed in a cantilever state in a horizontal posture on a machine base of a textile machine, an electric wire processing machine, or the like so as not to rotate. A shaft body 1, a rotation guide 2 that rotates in contact with the traveling linear body S, and a bearing unit B that is interposed between the shaft body 1 and the rotation guide 2 to reduce the rotation torque of the rotation guide 2. Is equipped with.

The rotary guide 2 is made of a ceramic material and has a substantially ring-like shape.
A guide groove 2a that guides the guide groove 2a is recessed over the entire circumference, and a slide contact portion 15 with which the linear body S slides is formed in the center of the guide groove 2a.

The bearing unit B is connected to the shaft end of the shaft body 1 by a nut 14 and is installed around the shaft body 1, and the first bearing element 3 is connected to the rotation guide 2 to rotate around the first bearing element 3. And a second bearing element 4 installed on the second bearing element 4, and the first bearing emerent 3 is lightly press-fitted into the second bearing element 4.
The bearing element 4 is fitted and coupled to the second bearing element 4.

Of the rolling bearings, a radial ball bearing of JIS-682ZZ is used as the first bearing element 3 in this example, and a radial ball bearing of JIS-682ZZ of the rolling ball bearings is fitted as the second bearing element 4. JIS-685ZZ that can be matched
Radial ball bearings are used.

The maximum rotational speed allowed by the first bearing element 3 is 112,000 rpm, which corresponds to the maximum rotational speed of the radial ball bearing of JIS-682ZZ, and the maximum rotational speed allowed by the second bearing element 4 is JIS-685ZZ. This is 48,000 rpm, which is equivalent to the maximum rotation speed of radial ball bearings.

The first bearing element 3 is fitted around the shaft end of the shaft body 1 and fixed to the first inner ring 5, and the first inner ring 5 is installed concentrically around the first inner ring 5 with a gap. The outer ring 6 and the first inner ring 5 and the first outer ring 6 are arranged in a planetary manner around the shaft 1 while being interposed between the first inner ring 5 and the first outer ring 6. And a first row of rolling elements 7 constituted by a plurality of rolling elements 8 to be reduced.

The second bearing element 4 has an inner diameter equal to the outer diameter of the first outer ring 6 of the first bearing element 3, and is fixed to the first outer ring 6 so as to surround the first outer ring 6. A second inner ring 9 that rotates together with the first outer ring 6; a second outer ring 10 that is installed concentrically around the second inner ring 9 with a gap and is fixed to the inner peripheral surface of the rotation guide 2;
The inner ring 9 and the second outer ring 10 are arranged in a planetary pattern around the first rolling element row 7 while being interposed between the inner ring 9 and the second outer ring 10. Second rolling element row 1 composed of a plurality of pairs of rolling elements 12 to be reduced
1 is provided.

The first rolling element row 7 of the first bearing element 3 and the second rolling element row 11 of the second bearing element 4 are loaded inside the bearing unit B in a state of being stacked in the radial direction of the shaft body 1. ing.

When the traveling linear body S contacts the rotation guide 2, the rotation guide 2 rotates in combination with the rotation torque attenuation performance of the first rolling element row 7 and the rotation torque attenuation performance of the second rolling element row 11. Due to the torque reduction effect, the linear body S rotates following the traveling speed.

Next, the second embodiment of the present invention shown in FIG. 3 will be described. In this embodiment, the rotation guide 2 of the guide tool G is used.
A is a guide groove 2a in which the sliding contact portion 15A is formed in the central portion.
It is formed by a first guide member 16 made of ceramics having A and a pair of second guide members 17 made of synthetic resin which are dividably coupled with the first guide member 16 sandwiched therebetween. The outside is constructed similarly to the first embodiment,
As the first bearing element 3 and the second bearing element 4 of the bearing unit B, the radial ball bearing of JIS-682ZZ and JI are used as in the first embodiment.
S-685ZZ radial ball bearings are used.

In the first and second embodiments, the maximum rotation speed of the rotary guides 2 and 2A is theoretically the maximum rotation speed allowed by the first rolling element train 7 of the first bearing element 3 is 112,000 rpm. Maximum rotational speed allowed by the second row of rolling elements 11 of the two bearing elements 48,000rp
The total number of revolutions added with m is 160,000 rpm.
The maximum peripheral speed of the sliding contact portion 15 (diameter 13.5 mm) of the rotation guide 2 of the embodiment is 13.5 mm × 3.14 × 160,000 rpm = 6782.4 m / min.
Therefore, the maximum peripheral speed of the sliding contact portion 15A (diameter 20 mm) of the rotation guide 2 of the second embodiment is 20 mm × 3.14 × 160,000 rpm = 1,0
48m / min.

On the other hand, the rotation guide having the same shape as that of the rotation guide 2 of the first embodiment and JIS-694ZZ.
In the conventional guide tool with the radial ball bearings (guide tool g shown in Fig. 7), the maximum rotation speed of the rotary guide is 52,000.
In rpm, the maximum peripheral speed of the sliding contact part (diameter 13.5 mm) of the rotary guide is 13.5 mm × 3.14 × 52,000 rpm = 2204.28 m / min
Becomes

Further, in the conventional guide tool having the rotary guide having the same shape as the rotary guide 2A of the second embodiment and the radial ball bearing of JIS-694ZZ, the maximum rotational speed of the rotary guide is 52,000 rpm, The maximum peripheral velocity of the sliding contact part (diameter 20mm) of the rotation guide is 20mm × 3.14 × 52,000rp
It becomes m = 3,265.6 m / mm.

Therefore, the two bearing elements 3,
The maximum rotation speed of the rotation guides 2 and 2A of the guide tool G having 4 is about 3 times the maximum rotation speed of the rotation guide of the conventional guide tool having one radial ball bearing, Sliding contact portions 15 and 15A of the guide grooves 2a and 2aA
The maximum peripheral speed of is about 3 times the maximum peripheral speed of the sliding contact portion of the conventional rotary guide.

The rotation guide 2 of the guide tool G of the first embodiment is
The rotation guide 2A of the guide tool G of the second embodiment is 10,000 when it follows the linear body S traveling at a high speed of 6,000 m / mm or more and follows the linear body S without slipping.
Following the linear body S traveling at a high speed at a traveling speed of m / min or more, the linear body S rotates at a high speed in a state in which the linear body S is slip-free.

Next, the rotation guide 2 of the guide tool G of this example
A comparison test performed to compare the starting torque between 2A and the conventional guide of the rotation guide will be described. In the measuring device used for measuring the starting load for calculating the starting torque, as shown in FIG. 6, the yarn (polyester monofilament) 30 is attached to the measured object (guide tool) 31 in an inverted U shape. Then, one end of the yarn 30 is locked to the distal end of the wire 32 having a slight bending elastic force with the base end fixed and the distal end released, and the other end of the yarn 30 is attached to the weight tray 33. On the weight saucer 33, keep 0.
The weights of 01 g are placed one by one, and each time the weight is placed on the weight tray 33, the tip of the wire 32 is lifted by hand to bend and deform upward, and the object to be measured 31 is activated at a certain point. And rotate a little.

A value obtained by adding the total weight of the weights placed on the weight tray 33 and the weight of the weight tray 33 (0.02 g) until the object 31 to be measured is the starting load of the object 31 to be measured. The starting torque of each DUT 31 is calculated based on this starting load.

Rotation guide 2 of the guide tool G of the first embodiment
Table 1 shows the measurement results of the starting loads of the rotating guide having the same shape as that of the rotating guide 2 and the rotating guide of the conventional guide tool provided with the JIS-694ZZ radial ball bearing for each of 10 materials. Show.

[0033]

[Table 1]

When the starting torque is calculated from the measurement results shown in Table 1, the starting torque average value of the rotary guide of the conventional guide tool is 1,080 mg × 13.5 mm / 2 = 7,290 mg − mm, which is the first value.
The average value of the starting torque of the rotary guide 2 of the guide tool G of the embodiment is 60 mg × 13.5 mm / 2 = 405 mg-mm, and the starting torque of the rotary guide 2 is about 1 / l of the starting torque of the rotary guide of the conventional guide tool. 18 (5.56%), and it was proved that the rotation guide 2 of the first embodiment started with a slight starting torque due to the effect of reducing the rotation torque of the bearing unit B.

Rotation guide 2A of the guide tool G of the second embodiment.
And a rotation guide having the same shape as that of the rotation guide 2A,
And the starting load with the rotation guide of the conventional guide tool having the JIS-694ZZ radial ball bearing is 1 respectively.
Table 2 shows the results of measurement for 0 samples.

[0036]

[Table 2]

When the starting torque is calculated from the measurement results shown in Table 2, the average value of the starting torque of the rotary guide of the conventional guide tool is 620 mg × 20 mm / 2 = 6,200 mg-mm, which is the guide tool G of the second embodiment. The average value of the starting torque of the rotating guide 2A is 37mg × 20mm / 2 = 370mg-mm.
The starting torque of is reduced to about 1/17 (5.97%) of the starting torque of the rotating guide of the conventional guide tool, and the rotating guide 2A of the second embodiment has a slight starting torque due to the effect of the rotating torque of the bearing unit B being reduced. Proven to start.

Therefore, according to the first and second embodiments, the rotation torque of the rotation guides 2 and 2A is greatly increased by using the existing first and second bearing elements 3 and 4 which can be fitted to each other. It is possible to reduce and stabilize the fiber yarns without stretching unevenness, uneven thickness, feathering, single fiber breaks, etc. even when the fiber yarns run at high speed or when starting to run. In addition, the electric wire can be stably run in a state in which the electric wire is free from disconnection and peeling of the insulating coating, even when the electric wire travels at a high speed and when the electric wire starts to travel.

Next, the third embodiment of the present invention shown in FIG. 4 will be described. In this embodiment, the bearing unit B is used as a bearing member for rotatably supporting the shaft body 20.

The first inner ring 5 of the first bearing element 3 having the first rolling element row 7 is rotatably coupled to the shaft end of the shaft body 20 and of the second bearing element 4 having the second rolling element row 11. The second outer ring 10 is fixed to a bearing case 21 that houses the bearing unit B.

The maximum rotation speed of the shaft body 20 is the rotation speed obtained by adding the maximum rotation speed allowed by the first bearing element 3 and the maximum rotation speed allowed by the second bearing element 4.

Next, the fourth embodiment of the present invention shown in FIG. 5 will be described. In this embodiment, in the rotation guide G including the shaft body 1, the rotation guide 2 and the bearing unit B,
Between the first rolling element row 7B and the second rolling element row 11B of the bearing unit B, and between the inner ring 23 and the outer ring 24 there is a first
The second rolling element row 1 is circumscribed to each rolling element 8B of the rolling element row 7B.
An intermediate wheel 25 inscribed in each rolling element 12B of 1B is installed in a state where both rolling element rows 7B and 11B are partitioned by this intermediate wheel 25, and the first bearing element 3B and the second bearing unit 4B are integrated. ing.

According to the fourth embodiment, since the intermediate wheel 25 is in a state in which the first outer ring 6 and the second inner ring 9 of the first embodiment are combined into one component, the number of components of the bearing unit B is reduced and the bearing The structure of the unit B can be simplified, the cost of the bearing unit B can be reduced, and the outer diameter of the bearing unit B can be reduced to make the bearing unit B compact and lightweight.

[0044]

According to the first aspect of the present invention, each rolling element row can exert a rotating torque damping effect combining the rotational torque damping performance of each rolling element row, which is allowed by the bearing unit. It is possible to synergistically increase the limit rotational speed and synergistically reduce the starting torque when starting the rotating body.

Further, when the rotating body is rotated at the limit rotational speed, the adverse effects due to the centrifugal force and the weight imbalance of the rolling elements become remarkable, and the heat generation lowers the viscosity of the lubricating oil, resulting in a rolling element row. However, if the rotating body is rotated at a safe rotation speed that is less than or equal to the limit rotation speed allowed by all rolling element rows, the movement and rolling speed of each rolling element in each rolling element row will be reduced. Since there is a margin for each, the service life of the entire bearing unit can be extended, and even if one of the rolling element rows fails in function, the other rolling element rows can reduce the rotational torque. Can be maintained.

According to the second aspect of the invention, the bearing unit is provided with the rotational torque reducing characteristic which is combined with the rotational torque reducing performance by the rolling element rows of the respective rows to synergistically increase the limit rotational speed of the rotary guide. The rotating body is rotated at a rotation speed that follows the traveling speed of the linear body traveling at high speed, and the linear body is smoothly traveling at high speed in a state where frictional resistance due to slip with the rotation guide is eliminated. The quality of can be stabilized.

Further, the starting torque at the time of starting the rotary guide is greatly reduced by the synergistic effect of reducing the rotary torque by all the rolling element rows, and the rotary guide is started with a slight starting torque at the start of traveling of the linear member. Therefore, it is possible to eliminate the problem that frictional resistance is applied to the filament due to the delay in starting the rotation guide.

According to the invention of claim 3, the number of parts of the bearing unit can be reduced to simplify the structure of the bearing unit and reduce the cost of the bearing unit, and the outer diameter of the bearing unit can be reduced to reduce the bearing. The unit can be made compact and lightweight.

[Brief description of the drawings]

FIG. 1 is an enlarged side sectional view of a guide tool showing a first embodiment of the present invention.

FIG. 2 is an enlarged side sectional view of a bearing unit.

FIG. 3 is an enlarged side sectional view of a guide tool showing a second embodiment of the present invention.

FIG. 4 shows a third embodiment of the present invention and is a side sectional view of a bearing mechanism using a bearing unit.

FIG. 5 is an enlarged side sectional view of a guide tool showing a fourth embodiment of the present invention.

FIG. 6 is a side view of a measuring device used for measuring a starting load.

FIG. 7 is an enlarged side sectional view of a conventional guide tool.

[Explanation of symbols]

 1,20 Shaft body 2,2A Rotation guide 3,3B, 4,4B Bearing element 7,7B 1st rolling element row 8,8B Rolling element 11,11B 2nd rolling element row 12,12B Rolling element B Bearing unit S line Article

Claims (3)

[Claims] 1. At least two rows of rolling element rows each having one set of rolling elements arranged around the shaft body are stacked in the radial direction of the shaft body and inserted inside. Bearing unit. 2. A guide tool having a non-rotatably installed shaft body and a rotation guide rotating in contact with a traveling linear body, wherein a set of rolling elements arranged around the shaft body. At least two rows of rolling elements each having the above are stacked in the radial direction of the shaft body and provided with a bearing unit installed inside. 3. An intermediate wheel, which circumscribes each rolling element in the inner rolling element row and inscribes in each rolling element in the outer rolling element row, is disposed between the two adjacent rolling element rows. 3. The bearing unit according to claim 1, wherein the bearing unit is installed in a state of being partitioned by the intermediate wheel, or the guide unit according to claim 2, comprising the bearing unit.