JP2640625B2 - Bearing fixing device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for easily and detachably fixing a bearing to a shaft portion of a rolling roll, and more particularly to a fixing device using hydraulic pressure.

[0002]

2. Description of the Related Art Most of conventional devices of this type are provided with a concave groove at the tip of a roll shaft, a split ring having an external thread on the outer periphery is fitted into the concave groove, and a nut is inserted into the external thread. And the thrust of the nut acts on the inner ring of the bearing via the cylindrical body, and the inner ring is pressed against the step of the shaft and fixed. The nut is fixed so as not to be loosened with a lock nut or a locking bolt. The cylindrical body fitted to the shaft transmitting the thrust of the nut to the inner ring also serves as a seal ring, abuts on the fixed side of the bearing via a seal, and is provided with a key for stopping rotation of the shaft. It is.
This key is necessary because if the cylindrical body, that is, the seal ring, slides between the shaft and rotates, it may cause inconveniences such as incomplete sealing, seizure with the inner ring end face, and loosening of the lock nut. It is something. However, since the inner ring is slidable and rotatable with respect to the shaft for attachment and detachment with respect to the shaft, there is also a configuration in which a side surface key is provided on an end face which comes into contact with the seal ring so as not to rotate. Such separation and assembly of the bearing device and the shaft are performed off-line (off-line) by removing both the roll and the bearing device from the rolling line, and the separation and assembly work is performed by a number of workers. It is necessary.

[0003]

The separation and assembly of the bearing device and the shaft has a problem in that a large shaft diameter requires a great deal of labor and time. In particular, in the work of attaching and detaching the nut, hitting with a hammer when loosening or tightening is performed, and there is a problem with danger. In addition, in the configuration using a locking bolt, a recess is provided at a position where it comes into contact with the tip of the bolt, but if the shaft changes, the position also changes each time, so it is difficult to securely tighten without any gap in the axial direction, Since this small gap causes the roll to move in the axial direction during rolling, there is a problem that product accuracy is adversely affected. In the configuration performed by tightening the lock nut, the nut tightening torque is not constant, so that there is a problem in that additional tightening is required for loosening due to operation. In addition, if an automatic machine is used to mount a bearing device having a fixing device on a shaft, a means for matching the key position of the bearing fixing device with the keyway position of the shaft is required, and automation can be easily performed. Some problems cannot be done. SUMMARY OF THE INVENTION An object of the present invention is to provide a bearing fixing device which can obtain a good tightening state and can be easily attached to and detached from a roll shaft.

[0004]

Means of the present invention According to an aspect of the push from the shaft end side of the inner ring of the bearings of the shaft end fitted with Amashi the axial end portion to a predetermined position of the axis of the roll A generally cylindrical main body slidably fitted to the shaft so as to transmit pressure, an engaging member detachable from an annular groove provided in a circumferential direction of the shaft is provided on the main body, An annular cylinder is formed coaxially in the body to accommodate the annular piston, and by supplying pressure oil to the annular cylinder, the annular piston engages the engaging member with the annular groove and presses it. The annular piston is provided with an engaging member driving unit, and the pressing is maintained by separating and holding a hydraulic oil in a state in which pressure oil is supplied to the annular cylinder.

[0005] In the above means, the engaging member protrudes from the inner peripheral surface of the main body and is pressed by the first spring and the clamp position engaged with the annular groove provided in the circumferential direction of the shaft, and is housed in the main body. It is preferable to use a plurality of devices that can rotate to the unclamping position. Also, a second spring that presses the annular piston from the shaft end side is provided, and the annular piston advances toward the shaft end side against the second spring by supplying pressure oil to the annular cylinder. It is preferable that an annular member is provided with an engaging member driving portion so that the engaging member is rotated from the unclamping position to the clamping position against the first spring and pressed in the clamping direction. It is preferable that one of the hydraulic couplers is provided such that a pressure oil passage end in the main body that supplies and discharges pressure oil to and from the cylinder faces an end surface of the main body on the shaft end side.

In the above means, one end is fixed to a fixed side of a chock provided with the bearing and formed in a cylindrical shape surrounding the main body with a small gap therebetween, and the main body is detached from the shaft in a state where the chock is removed. It is preferable to provide a holding body for holding on the chock side.

[0007]

According to the means of the present invention, when the pressurized oil is supplied to the hydraulic cylinder of the fixing device fitted to the shaft together with the bearing device, the engaging portion engages with the annular groove of the shaft and the counterpart from the annular groove. The main body presses the inner ring of the bearing from the shaft end side by force to be in a fixed state. Since this fixing state is based on the hydraulic pressure, it is forcibly pressed and can be fixed sufficiently strong without any gap. Thereby, the key between the fixing device main body and the shaft can be omitted.
Since the hydraulic cylinder is an annular cylinder surrounding the shaft,
It can be used with low oil pressure. Since the configuration in which the second spring is provided retreats the piston when the pressure oil is drained, the cylinder may be a single-acting type and may have one pressure oil supply / discharge port. When the piston retreats, the engagement portion returns to the unclamped position by the first spring. Therefore, in attaching and detaching the bearing,
A pressure oil passage is connected to the pressure oil supply / discharge port, and pressure can be applied or discharged to make it clamped or unclamped so that it can be detached. The configuration in which one of the hydraulic couplers is provided with the hydraulic oil passage end inside the main body facing the shaft end side end surface of the main body is configured to connect and disconnect the coupler at the shaft end side , so operability is good and automation It is appropriate and balances weight at high speed rotation
Good. On the other hand, the pressure oil supply / drain
If the weight is set, the weight balance during rotation will be poor,
In addition, there is a problem in use at high speed rotation. When the bearing device and its fixing device are fitted to the shaft when the bearing device and the fixing device are mounted on the shaft, the bearing device is positioned coaxially with the shaft and moved in the axial direction. Both fixing devices can be fitted in one operation.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described with reference to FIGS. The bearing fixing device 1 includes a main body 2, an engaging member 3, an annular cylinder 4, an annular piston 5, an engaging member driving unit 6, a male coupler 7, and the like.
The inner ring 10 of the thrust bearing 10 which are respectively mounted on a
The is obtained so as to press secured using annular groove 12 of the shaft end portion of each of the shaft end side. As shown in FIG. 6, the shaft 9 has a portion 9a where radial bearings 11 are provided on both outer sides of a body diameter portion 8a, a portion 9b where a thrust bearing 10 and a bearing fixing device 1 are provided outside thereof, and a portion 9b outside the portion. One end (right side in FIG. 6) has an annular groove 12 and a two-plane width portion 13 as a rotation driving portion when using a roll.
Is formed as an extension. 6, the portion indicated by the phantom line is chock assembly 14, Surasutobe bearings 1
0 , a radial bearing 11 and a bearing fixing device 1 are assembled.

The main body 2 of the bearing fixing device 1 is formed in a substantially cylindrical shape with an inner cylindrical portion 21, an outer cylindrical portion 22, an end ring 23 and the like. As shown in FIG. 1 showing the fixed state of the bearing, the inner cylindrical portion 21 has an inner hole 24 which is slidably fitted to the portion 9b of the shaft 9, and the end of the portion 21a on one side in the axial direction is formed. A portion 21b that fits into the inner hole of the inner ring 10a of the thrust bearing 10, extends toward the portion 9a of the shaft 9 and terminates without abutting on the step portion of the shaft, and protrudes in a flange-like shape on the outer periphery along the way.
And the end of the portion 21c on the other side in the axial direction is the annular groove 1
It has reached a position slightly over 2. The portion 21b has an abutting surface 25 that abuts on the axial end surface of the inner race 10a and an outer peripheral surface 27 that abuts the seal 26, and also forms an end wall of the annular cylinder 4 described later. The portion 21a is omitted so that the inner hole of the inner ring 10a is directly fitted to the outer periphery of the inner ring 10a by thickening the shaft 9b or the like. May be transmitted. However, the chock assembly 1 from the shaft 9
Since the axis of the inner ring 10a of the thrust bearing 10 and the axis of the fixing device main body 2 are displaced in a state in which the shaft 4 is removed, the portion 21a is preferably provided if importance is placed on the operability of fitting the shaft. The outer cylindrical portion 22 is disposed on the outer periphery of the portion 21c with a gap therebetween, and one end is fixed to the portion 21b with a bolt 28.
Te unit component 21b, forms an annular cylinder 4 by the 21c, the other end has reached the end of the shaft 9. Although it is conceivable that the portions 21b and 21c of the inner cylinder portion 21 are formed separately, that is, they may be formed separately in the inner cylinder of the annular cylinder 4 and the cylinder head. , The manufacturing error of each part is accumulated,
Since the variation in the dimension indicated by L in the figure becomes large, the engagement state between the engagement member 3 and the annular groove 12 may be adversely affected, and it is preferable to form them integrally. End ring 23 is shaft 9
The inner cylindrical portion 21 and the outer cylindrical portion 22
Are fixed to each other with bolts 29 and 30 (see FIGS. 1 and 2) so as to close the gap.

As shown in FIGS. 1, 2, and 5, four engaging members 3 are provided in the main body 2 at equal intervals in the circumferential direction, and are rotatably supported by the end face ring 23. Its shape is
As can be understood from the figure, the shaft portion 3 whose shaft has penetrated the large diameter portion
The arm 3b extending from the large diameter portion is provided with a claw 3c that engages with the annular groove 12. The claw 3c is formed in an arc shape corresponding to the annular groove 12. Shaft 3a
Is rotatably disposed in a recess 31 provided in the end face ring 23 as shown in the figure, and the arm 3b and the claw 3c are
The outer cylinder 22 is rotatable in a range extending over the gap between the outer cylinder 22 and the notch 32 formed in the inner cylinder 21 and the annular groove 12. As a result, as shown in FIG. 1, the engagement member 3 has the claw 3 c protruding into the inner hole 24 of the inner cylindrical portion 21 and the annular groove 1.
The clamping position engaged with the side surface 12a on the shaft end side of the main body 2 does not protrude into the inner hole 24 as shown in FIG.
It is rotatable to an unclamped position that is housed within. As shown in FIG. 5, a first spring 33 is provided between the pawl 3c and the end face ring so that the engagement member 3 rotates to the unclamping position when an annular piston 5 described later is retracted.
Are interposed in a compressed state. In the figure, reference numeral 34 denotes a screw for inserting and fixing a spring.

As described above, the annular cylinder 4 includes the portions 21b and 21c of the inner cylinder 21 and the outer cylinder 22 inside the main body 2.
Is formed by As shown in FIGS. 1, 3, and 5, the annular piston 5 includes an inner cylindrical portion 21 and an outer cylindrical portion 2 of the main body 2.
2, that is, a short cylindrical shape which is slidably accommodated in the annular cylinder 4 in the axial direction so as to be slidable in the axial direction. Is determined so that it can rotate until it comes into contact with the inner peripheral surface of the outer cylinder portion 22, that is, does not interfere with the claw 3c. On the engagement member 3 side of the annular piston 5, in order to obtain easy rotation of the engagement member 3, the tip of the engagement member drive unit 6 is formed as a round surface 35 having a convex circular cross section in the axial direction as shown in the figure.
And a slope 36 is provided in the inner diameter portion. The driven surface 37 and the lock engagement portion 38 are provided on the claw 3 c of the engagement member 3.
Is provided. When the annular piston 5 advances while the engaging member 3 is at the unclamping position, the round surface 35 pushes the driven surface 37 of the engaging member 3 to rotate the engaging member 3 downward, and the piston 5 further moves. When moving forward, the slope 36 comes into contact with the lock engagement portion 38, and is in a state of rotating to the clamp position. The state in which the slope 36 of the annular piston 5 is in contact with the lock engagement portion 38 is a lock state in which the engagement member 3 cannot rotate in the direction of the unclamping position.

The rear side of the annular piston 5 is a pressure chamber 39, and the annular piston 5 is advanced toward the claw 3c of the engaging member 3 by supplying pressure oil.
Further, the four engaging members 3 are provided on the front edge of the annular piston 5.
Position between the respective (as seen in Figure 2 there places 4)
In, is notched abutment 40 it be shown in FIG. 1 formed at three positions, notched avoid interference with the block 46 to be described later to the remaining one location recess 40 a (shown in FIG. 4) Formed on the end face ring 23 at a position facing each of the contact portions 40.
1, be formed a field I support recess 41 as shown in FIG. 4, Oh Ru is provided a second spring 42 of a coil spring 3 ing in a compressed state. Reference numeral 43 in FIGS. 1 and 4 denotes a spring receiver. The spring receiver 43 also serves as a stopper for preventing rotation of the annular piston 5 during the forward / backward movement. Pressure chamber 39
As shown in FIGS. 3 and 4, a passage 44 is provided in the portion 21c of the inner cylinder portion 21 so that one end of the passage 44 communicates with the rear portion of the annular cylinder 4, and Is connected to an inner hole 47 of a block 46 to which the male coupler 7 is attached, and the male coupler 7 is located in an operation hole 48 formed in the end ring 23 toward the outside of the shaft end. The positions of the operation hole 48 and the block 46 are positions facing the recess 40a as shown in FIGS. Although not shown, the female coupler connected to the male coupler 7 is connected to a hydraulic oil supply / discharge passage switched by a switching valve to an appropriate hydraulic pressure source and a tank, and a predetermined advance / retreat driving unit is connected. When the female coupler is used to push the female coupler into the operation hole 48, the connection state is established. The coupler used here has a residual pressure release mechanism.

When pressure oil is supplied to the pressure chamber 39,
The annular piston 5 moves forward against the second spring 42 and
The engagement member 3 is rotated to the clamp position against the spring 33, and when the pressure oil is discharged, the annular piston 5 is retracted by the pressing force of the second spring 42 and the pressing force of the first spring 33 is pressed. , The engaging member 3 is rotated to the unclamping position. In FIG. 1, reference numeral 15 denotes a holder, which is a chock assembly 14 in a state where the outer periphery of the main body 2 of the bearing fixing device 1 is surrounded by a small gap.
Of the thrust bearing 10 is fixed to the retainer 50 of the outer ring 10b. In addition, an annular convex portion 51 is protruded at an appropriate position on the inner peripheral surface, and the convex portion 51
Are opposed to each other with a small gap therebetween. This hold
In the state where the chock assembly 14 is removed from the shaft, the body 15 is in a state in which the portion 21a of the main body is supported by the inner ring 10a of the thrust bearing 10, and the portion 21a is omitted. In the case of the structure, since it is not brought into a reliable supporting state only by abutting at the seal 26, the supporting is assisted and the retaining function is provided. Further, the holding body 15 also functions as a cover of the bearing fixing device 1.

The thus configured bearing fixing device 1 is used for the roll 8 shown in FIG. 6 as follows, for example. First, when the bearing is mounted and fixed, the roll 8 is placed on a roll support table which supports the body 8 in contact with the body diameter portion 8a so that the axis is horizontal. A chock support for supporting the chock assembly 14 which can be moved back and forth in the direction of the roll axis is prepared.
Is aligned with the axis of the chock assembly 14 and the pressure chamber 39 is previously depressurized, that is, in an unclamped state in which the pressure oil is discharged, and the chock assembly 14 is moved in the direction of the axis to move the Fit. Then, the female coupler is advanced and pushed into the operation hole 48 to connect with the male coupler 7, and pressurized oil is supplied to the pressure chamber 39 to increase the pressure. Pressure chamber 3
When the pressure is increased, the annular piston 5 advances as described above to rotate the engaging member 3, and the claw 3c
And is locked by engaging with the side surface 12a on the shaft end side. When the coupler is disconnected, the built-in check valve closes and the inside of the pressure chamber 39 is maintained at the pressure of the supplied pressure oil. When removing the chock assembly 14 from the roll 8, the procedure may be substantially reversed.

In the fixed state of the bearing, the reaction force from the engaging member 3 engaged with the annular groove 12 is applied to the thrust bearing from the contact surface 25 of the portion 21b by the extension action of the hydraulic cylinder composed of the annular cylinder 4 and the annular piston 5. The power is transmitted to the inner ring 10a of the shaft 10, and further reaches the step of the shaft portion 9b via the collar 52 and is received by this step, so that it is strongly fixed in the axial direction. The axial acting force is obtained by applying hydraulic pressure and can be considerably increased. The greater the greater, the greater the frictional resistance against the rotational force at each contact surface. By appropriately selecting the pressure receiving area and the used oil pressure, a sufficiently strong rotation stopping means can be obtained. That is, the bearing fixing device 1及beauty Sula
The inner ring 10a of the strike bearing 10 can be prevented from rotating with respect to the shaft 9. The state of the bearing fixing device 1 with the chock assembly 14 removed from the shaft 9 is such that the annular piston 5 is retracted, the engaging member 3 does not protrude inward from the inner hole 24 of the main body 2, and the bearing fixing device 1 is held. It is held by the body 15. And the fixing device 1 and the thrust bearing
The axis of the inner ring 10a of 10 coincides with the presence of the portion 21a, so that the operation of fitting the chock assembly 14 to the shaft 9 is easy.

The mounting of the bearing fixing device 1 is completed by the operation of connecting the coupler, supplying the pressure oil, and disconnecting the coupler after the chock assembly 14 is fitted on the shaft. Therefore, since an operation of tightening with a screw is not required, there is no hammer work, there is little danger, and labor can be reduced. In addition, when the chock assembly 14 is fitted to the shaft 9, there is no key and no key groove, so that there is no need to align the position, the workability is improved by that amount, and even in the case of mechanization, it is simple. Can be configured. In addition, this bearing fixing device 1
In the bearing, the inner ring of the bearing is tightened and fixed by the pressing force of the hydraulic pressure in the axial direction in the fixed state of the bearing, and is not tightened with the screw. And since there is no gap, the roll does not move in the axial direction during use, and the accuracy of the rolled product can be improved.

[0017]

According to the first aspect of the present invention, since the fixing state is based on the hydraulic pressure, there is no gap as in the conventional screw structure, and the fixing can be performed sufficiently strongly.
Since the key between the fixing device main body and the shaft can be omitted, the attaching / detaching operation can be simplified, and since it does not depend on screws such as nuts,
Since there is no need for overtightening and the hydraulic cylinder is an annular cylinder surrounding the shaft, it can be formed compact without bulk.
Further, there is an effect that the automation of the chock attaching / detaching device can be promoted. According to the second aspect of the present invention, since the cylinder is a single-acting type, only one pressure oil supply / discharge port is required, and the pressure oil supply / discharge port is provided in the main body without providing the pressure oil supply / discharge port on the outer periphery of the fixing device. As a result, the balance at the time of rotation is good, and it can be applied to high speed use,
Moreover, since the coupler is connected and disconnected on the shaft end side, the operability is good and an effect suitable for automation of the chock attaching / detaching device is achieved. According to the third aspect of the present invention, the bearing device and the fixing device thereof can be coaxially positioned by the presence of the holding member, and the bearing device can be fitted to the shaft together with the fixing device in one operation. To play.

[Brief description of the drawings]

FIG. 1 is an AOB cross-sectional view of FIG. 2 showing a main part of a state in which a bearing device is fixed to a shaft according to an embodiment of the present invention.

FIG. 2 is a side view of the same embodiment as seen from a shaft end portion in a state where the bearing device is fixed to the shaft.

FIG. 3 is a sectional view taken along line OC of FIG. 2;

FIG. 4 is a sectional view taken along line DD of FIG. 3;

FIG. 5 is a cross-sectional view of the OE cross section of FIG. 2 with the engaging portion in an unclamped state.

FIG. 6 is a front view showing a roll provided with a shaft to which the embodiment is applied.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Bearing fixing device 2 Main body 3 Engaging member 3a Shaft 3b Arm 3c Claw 4 Annular cylinder 5 Annular piston 6 Engaging member drive 7 Male coupler 8 Roll 9 Shaft 10 Thrust bearing 10a Inner ring 11 Radial bearing 11a Inner ring 12 Annular groove 14 Chock assembly 15 Holder 25 Contact surface 26 Seal 33 First spring 39 Pressure chamber 42 Second spring 44 Passage

 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-6-307459 (JP, A) JP-A-7-223005 (JP, A) JP-A-8-1216 (JP, A) 186004 (JP, U) Japanese Utility Model 1983-166907 (JP, U) Japanese Utility Model Application Hei 5-53707 (JP, U) Japanese Utility Model Application Hei 5-22325 (JP, Y2)

Claims (3)

(57) [Claims] An inner ring of a bearing at an end of a shaft fitted to a predetermined position of a shaft of a roll with an excess of an end of the shaft slides on the shaft so as to transmit a pressing force from the end of the shaft to the inner ring. A substantially cylindrical main body fitted as possible, an engaging member capable of being disengaged from an annular groove provided in a circumferential direction of the shaft is provided in the main body, and an annular cylinder is formed coaxially in the main body. The annular piston is housed, and an annular member is provided with an engagement member drive unit such that the annular piston engages the annular member and presses the annular member by supplying pressure oil to the annular cylinder,
A bearing fixing device, wherein the pressing is maintained by keeping the state in which pressure oil is supplied to the annular cylinder separately from a hydraulic pressure source. 2. A roll is attached to and detached from a shaft of a roll shaft so that a pressing force is transmitted from an end of the shaft to an inner ring of a shaft end side bearing which is fitted to a predetermined position of a shaft of the roll with an excess of the shaft end. A main body having a substantially cylindrical shape fitted to the main body is provided. The main body is pressed by the first spring and a clamp position which protrudes from the inner peripheral surface of the main body and engages with the annular groove provided in the circumferential direction of the shaft. A plurality of engagement members rotatable with the unclamped position are provided in the main body, an annular cylinder is formed coaxially in the main body to accommodate the annular piston, and the annular piston is moved from the shaft end side. A pressing second spring is provided, and by supplying pressure oil to the annular cylinder, the annular piston advances toward the shaft end side against the second spring to move the engaging member to the first spring. From the unclamping position to the clamping position against An engagement member drive section is provided on the annular piston so as to press in the ramp direction, and a hydraulic oil passage end in the main body for supplying and discharging pressurized oil to and from the cylinder faces an end surface of the main body on the side of the shaft end. A bearing fixing device comprising one of couplers. 3. The bearing fixing device according to claim 1, wherein one end is provided on a fixed side of a chock provided with the bearing and formed in a cylindrical shape surrounding the main body with a small gap therebetween. A bearing fixing device provided with a holding body which is fixed and holds the main body on the choke side in a state where the chock is removed from the shaft.