JPS5925791Y2 - Roller that provides uniform pressure - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a roller that can obtain uniform pressure over the entire length of the roller, which is suitable for transporting wide fabrics and the like.

This roller consists of a single non-rotating main shaft and a roller that rotates around the outer periphery of this main shaft and is connected at a small distance in the axial direction, so it consists of several roll members. It consists of

Each of the roll members is supported by the main shaft through a ring bearing device, and each bearing device has a fulcrum on the pressure medium housed in the main shaft.

The individual roll members provide a uniform force on the track.

Due to the spacing between the roll members, the main shaft can be deflected a little, and by doing so, the main shaft can perform a rolling operation over a wide width laterally to the driving track while adjusting the pressure by appropriately arranging the main shaft. You can help make this possible.

Canadian Patent No. 1 for such a roller There is one shown in No. 814172.

According to this document, the roll member is supported by a ball bearing or a roller bearing, and the inner ring of the bearing has a fulcrum on the main shaft through a leather-covered pressure cushion arranged at an angle of 90 degrees. It can move freely on the pressure cushion.

Such rollers cannot exhibit satisfactory performance when operated at high speed and subjected to strong forces.

The reason for this is that the ring bearings that are supposed to transmit the force are simply based on a shaky foundation, which tilts in all directions, causing adjacent bearings to have elements that move into unfavorable positions or vibrate. This is because it may cause

The object of the present invention is to obtain a roller that can guarantee stable operating conditions even when a high load is applied and the struts of the ring bearing device are tilted radially.

The solution to this problem is the guide of the present invention, which allows the individual ring bearing devices to move freely in the radial direction in response to the pressure of the pressure medium, and during this movement, the ring bearing The device is drawn towards the main axis.

The rollers are then no longer completely free, but are linearly constrained to the spindle, restricting the free movement of the roll members in directions other than the desired radial direction. be.

This restriction also reduces the possibility of the appearance of unwanted vibrations.

Therefore, the entire device is stable, so that the roll section can operate quietly under various working conditions, which stability is especially required for high-speed operation.

The first guide embodiment mentioned consists of a swivel bearing lying outside the axis of the ring bearing arrangement and having an axis parallel to the axis of the ring bearing arrangement, whereby the ring bearing arrangement is based on the main shaft. have it.

At this time, the ring bearing device may collide with the main shaft on a plane perpendicular to its own axis and the axis of the roll.

This movement is caused by the force of the pressure medium and, when balanced, is limited to this.

Here, a portion of the swivel bearing may be fixed to the outside of the main shaft, and the other portion may be fixed to a bushing that supports the inner ring of the ring bearing device.

Therefore, the inside of the ring bearing device is connected to the main shaft like a hinge.

Although this is a structural problem, this method also reduces manufacturing costs.

Moreover, this method is very effective in restricting the freedom of movement of the ring bearing device.

It has also been established that vibration-free operation of a ring bearing arrangement supported by a pressure medium can be achieved.

Another guide embodiment to consider is a straight guide bearing arrangement that supports a ring bearing arrangement and is arranged on the main shaft.

This straight guide bearing arrangement more strictly limits the radial movement allowed by the ring bearing arrangement.

This may be required in special cases.

Of course, the manufacturing cost of a straight guide device is a little higher than that of a swivel bearing device.

The straight guide bearing arrangement is fitted with a shaft connected to the ring bearing arrangement and arranged radially of the main shaft, which shaft can be inserted into a bushing fixed to the main shaft.

This shaft therefore moves in the radial direction together with the ring bearing arrangement.

This shaft also allows the ring bearing arrangement to be anchored directly on the pressure medium.

In this case, the shaft not only functions as a guide, but also has the ability to transmit force.

In this arrangement, the shaft is a piston with a hole closed to the bushing, the end of which does not contact the ring bearing directly adjoins the pressure medium, the pressure of which causes the piston to move.

Straight guide bearings are equipped with straight guide rails arranged on both sides of the main shaft and running perpendicular to the center line of the mutually parallel main shaft, along which the guide elements move.

The guide rail is connected to a main shaft or a ring bearing arrangement.

The guide element, on the other hand, sits on whichever of these two parts the guide rail is not connected to.

Guide elements consist of rollers, sliding objects, rails, etc. that run along the guide rail.

This is straight parallel to the guide rail, and is supported by a sliding mechanism such as a bearing needle, so it can move.

The simple and purposeful structure of this invention, which uses a swivel bearing as a guide, is that the piston operates essentially perpendicular to the plane formed by the vertical bisector of the main shaft and the axis of the swivel bearing. , are provided in each individual ring bearing device.

One end of the piston is supported by a ring bearing arrangement and the other end by a pressure medium.

Canadian Patent No. 814 states that the case containing the pressure medium includes a pressure cushion having a resilient outer surface.
This is a well-known fact as stated in No. 172.

A force-conducting element contacts this resilient wall.

If the pressure at one location increases, it is conducted throughout the pressure medium, so that the pressure relationship can always remain in equilibrium.

Gas or liquid may be used as the pressure medium.

Several pressure cushions may be arranged along the main axis, but these pressure media must be connected to each other.

In this way, when one pressure cushion is deformed, the pressure medium contained in that cushion flows into the other pressure cushions, and the pressure cushions are combined into one pressure cushion as a whole.

A particularly simple embodiment is to make one long leather-wrapped pressure cushion along the main axis.

This embodiment has particular significance in connection with guides designed as swivel bearings.

That is, in this case, the screw I/N can have a fulcrum directly on the leather-covered pressure cushion.

Along the length of the roll, the screws attached to the individual ring bearing arrangements stand bone-like against a leather-like pressure cushion.

This creates a row of depressions in the cushion, but since the pistons are all made to the same shape and have the same diameter that exerts pressure, they all receive the same force.

The case containing the pressure medium may also be made of solid walls.

In this case, if a hole is made in the wall surface and the hole is closed with a flexible pressure element, only a certain part will become flexible, and if a change occurs in this part, that change will be transmitted to the attached ring bearing device. Ru.

In some embodiments of the piston, the pressure element expediently rests directly on this case.

The pressure element can also be made, for example, of a membrane that closes the hole and is flexible in the direction perpendicular to the hole.

Contemplating other embodiments, the pressure element arranged in the opening can be made of a flexible bellows in the direction perpendicular to the opening.

In each of the embodiments described above, the case for the pressure medium is formed within the main shaft, and the main shaft is provided with a hole for receiving an element for transmitting pressure to a ring bearing arrangement on the outer periphery of the main shaft.

This is one of the features of the present invention.

Since the ring bearing device surrounds the main shaft, the cross-sectional area of the main shaft, which determines the bending resistance of the roll, is limited by the inner diameter of the ring bearing device.

Here, if the pressure medium case is housed between the main shaft and the ring bearing device, the cross section of the main shaft will become smaller.

However, if the pressure medium case is housed inside the main shaft,
The main axis expands radially as much as possible without losing strong bending resistance.

In a preferred embodiment of the invention, the main shaft is pipe-shaped and the leather-wrapped pressure cushion runs through the inside of the pipe and extends over the entire length of the pipe.

This construction has two advantages: simplicity and, in particular, the ability to insert and remove the pressure cushion without disassembling the roll member.

Also, if the main shaft is made of a real pipe, the inside of the pipe itself can be used as a pressure case.
In this case, a hole is made in the wall of the pipe and this hole is closed with a flexible pressurizing element.

If the track or roll runs and rotates on the roll according to the invention, the pressure of the track or the weight of the roll balances the force exerted on the ring bearing arrangement by the pressure medium.

The track or roll is smaller than the length of the roller, but when it is short, some of the outer roll members do not contact the track or roll and are not subjected to these forces, but the roll members absorb all of the pressure medium. Even though it is under pressure, there is no counter pressure to counter it.

Therefore, if you want to avoid excessive changes in the position of the outer roll member with respect to the main shaft, it is recommended to provide a pressure release chamber that can be punched out independently on the side that is not receiving pressure of the corresponding outer ring bearing device. good.

This is because the pressure medium shared by all roll members compensates for the force exerted on a roll member that has never been loaded, and by balancing the load pressure with the force exerted by the pressure medium, the force applied to the other roll members is compensated. It stabilizes the ring bearing device in an equilibrium state.

Advantageously, a supply conduit is attached to the main shaft inside the ring bearing arrangement, so that lubricant can be conveyed to the ring bearing arrangement.

The supply opening is rotatably mounted on the outside of the main shaft, from which a nozzle projects laterally in the area of the ring bearing arrangement.

During assembly, the nozzle of the supply port should be brought into close contact with the main shaft.

The ring bearing device then passes over it.

On the other hand, during operation, the nozzles protrude radially and spread lubricant near the ring bearing.

When the tension of a running track with a large contact angle is not very strong, such as a running track of paper, the roll member needs to be particularly nimble in order to rotate all the way in an orderly manner.

In such cases, it is recommended to spray lubricating oil onto the ring bearing arrangement.

This is because ring bearing devices require only a small amount of lubricating oil, and when a normal head is applied, there is no residual resistance due to its viscosity, although it is small.

Here, the expression "ring bearing device" is a comprehensive term considering all kinds of bearings for each roll member.

Typically, each roll member rotates on a centrally located roller bearing lug.

However, when many roller bearings are arranged in parallel,
Other embodiments such as pole bearings are also possible.

These several bearings are based on one common part, for example a bushing, or this bushing is subjected to a force exerted by a pressure medium.

Since the type and configuration of the arrangement of the bearings that support the individual roll members have no essentially important meaning for the present invention, they are collectively referred to as a "ring bearing device."

Embodiments of the present invention will be described below based on the drawings.

The roller depicted in FIG. 1 includes a main shaft 1 in the form of a hard hollow shaft.

The main shaft 1 is fixed to a base via a ball bearing 3 having a surface 2.

In the ball bearing, the surface 2 does not prevent the main shaft 1 from deflecting.

Deflection of the main shaft 1 occurs naturally when a load is applied to the roller, but it can also be caused intentionally.

This deflection occurs, for example, when using wide rollers, see FIGS. 12 and 13.

Further, the bearing 3 does not prevent the main shaft 1 from rotating about its axis so that when the main shaft 1 is deflected, it can move according to the direction of the deflection.

A plurality of roll members 4 located on the main shaft 1 concentrically surround the main shaft 1 and are closely connected in the axial direction.

However, there are small gaps between the individual roll members 4.

This allows the cylindrical arrangement formed by the entire roll member 4 to flex, and at the same time, the roll member 4
The corners of the two do not touch each other.

When using a roller to wind up paper, the gap must be kept as narrow as possible, less than 1 mm, otherwise the paper may get stuck in the gap and cause wrinkles.

The roll member 4 may be made of any suitable material such as iron, aluminum, or plastic.

Alternatively, the entire series of roll members 4 may be covered with a single sealed case 5 made of a flexible material.

Only its outline is shown in Figure 1.

A ring bearing device 6 is attached to each roll member 4 .

This is made of a ball bearing having an outer ring 7 and an inner ring 8, as shown in the embodiment.

Here, the outer ring 7 is adjacent to each inner circumference, and the inner ring 8 is supported by a bushing 9.

This bushing 9 is a support for the roll member 4 and also serves as a guide.

The non-long bearing device 6 may be a simple ball bearing.

Of course, roller bearings and other types of bearings other than pole bearings can also be considered.

As can be seen from FIGS. 2 and 3, the ring bearing arrangement 6 and therefore the roll member I are connected to the main shaft 1 via a guide.
It is in contact with

- The guide is a person who forms the swivel bearing 10. This swivel bearing 10 consists of two bearing pedestals 11, and this bearing pedestal 11
is screwed to the main shaft 1, and the ball bearing 12
It supports the shaft 13 that spans.

1' This shaft 13 is directly connected to the bushing 9 of the ring bearing arrangement 6.

, top push 9
The inner diameter of the main shaft 1 is larger than the outer diameter of the main shaft 1, and within this limit the inner diameter of the main shaft 1
The bushing 9 can pivot around a bearing shaft 13 that is in contact with the bearing shaft 13.

Due to this movement, the roll member 4 begins to move in a direction perpendicular to the main shaft 1.

Inside the main shaft 1, there is a pressure cushion 1 shaped like a leather covering.
5 is provided, the ends of which are closed by end portions 16, in which a pressure medium, for example oil, is accommodated.

A through hole 17 is located in the peripheral wall of the main shaft 1 at a location that coincides with the roll member 4.
is open.

A piston 18 screwed onto the bush 9 of the ring bearing device 6 passes through the through hole 17 and presses against the leather-covered pressure cushion 15.

The axis of the piston 18 stands in a direction perpendicular to the plane defined by the longitudinal bisector 19 of the main shaft 1 and the bearing axis 13.

The paper 20 running on the running path exerts a constant force 21 on the roll member 4 due to its own tension, and this force applies torque to the bearing shaft 13.

This torque is corrected by the pressure medium in the pressure cushion 15 and acts as a reaction force 22 on the piston 18.

This force, if balanced, imparts an equal amount of torque in the opposite direction around the bearing shaft 13.

The loading capacity of the rollers can be varied by adjusting the pressure in the pressure cushion 15.

The pressure in the pressure cushion 15 is propagated uniformly over the entire length of the main shaft and the piston 18 connecting to the individual roll member 4
Since each has a surface that exerts the same amount of pressure, the roll members 4 all obtain the same amount of reaction force and accordingly apply uniform pressure to the running path of the paper 20.

When the roll is a wide roll facing paper,
The close contact surface between the roll member 4 and the paper surface 20 is not very large, and the ring bearing device is required to operate easily.

For this reason, in this embodiment, a supply pipe 23 (FIG. 2) extending along the main shaft 1 is provided as an oil spraying device.

This oil spraying device has a nozzle 24 protruding from a supply pipe 23, and sprays oil onto the rotating portion of the ring bearing device 6.

Since the supply pipe 23 is a rotating pipe, the nozzle 24, which is drawn in thin lines in FIG.

When the installation is completed, the supply tube 23 is rotated and the nozzle is drawn out, but in a radially protruding position.

Naturally, the sprayed oil should be prevented from coming out of the roll.

Otherwise, the sprayed oil will stain the roller surface.

For this reason, a gap filling bellows 25 is provided between the roll member 4 at the end of the roll and the main shaft 1, and each gap device 2 of each roll member 4 is
6 each.

This gap filling device 26 also serves as a transmission member that transmits the rotational moment (torque) of the roll member 4 to the adjacent roll member 4.

FIGS. 4 and 5 each show another embodiment, which differs from the previous embodiment in the structure of the pressure medium storage chamber.

That is, in this embodiment, the pressure medium storage chamber is a pressure chamber with hard walls, a hole is made in the wall surface, and an element that can bend in a direction perpendicular to the wall when the force of the pressure medium is applied is trapped. It is.

In FIG. 4, the main shaft 1 itself forms a receiving chamber for the pressure medium.

The main shaft 1 has an opening 27, which is formed by a bellows 28.
is blocked by.

The pressure of the pressure medium receiving chamber acts on its floor plate 29 and is transmitted through the piston 18 to the ring bearing arrangement 6.

The embodiment visible on the left side of FIG. 4 is a modified example, in which the opening 2
A cylinder 30 that reaches the inside of the main shaft 1 is fixed to 7, and the inside bottom surface thereof is a membrane 31.

The pressure medium acts on the outside of the membrane 31 and the inside of the membrane 31 supports the piston 18, so that the pressure in the pressure medium receiving chamber is transmitted through the piston to the ring bearing arrangement 6.

In the one in FIG. 5, a pressure groove 32 is formed in the main shaft 1, and in the one on the right, the opening 33 is closed with a bellows, and the floor plate 3 is
5 acts on a piston 18, which is connected to a ring bearing arrangement.

The one shown on the left side of FIG. 5 has a membrane 36 instead of the bellows 34.
That is.

In each of the embodiments shown in FIGS. 1 to 5, the point of application of the force is on the vertical bisector 19 of the main axis 1. In the embodiments shown in FIGS.

Since the force acts on the bearing shaft 13 as a tangential force fairly accurately, even if the position of the piston 18 is changed, the point of action will be shifted relative to the action surface, that is, relative to the outside of the pressure cushion 15. , with respect to the floor plate 29.35 and with respect to the membrane 31.36, no substantial deviation occurs.

FIGS. 6 and 7 show a further embodiment in which the guide of the roll member 4 is connected to a linear guide bearing 40.
This is different from each of the embodiments described above.

The linear guide bearing 40 has a shaft 41 which is arranged parallel to each other with a constant distance, one end of which is screwed into the bushing 9 of the ring bearing arrangement 6, and the other end of which is provided with a mushroom-shaped head 43. It's a formality.

This shaft 41 is movable radially forward and backward with respect to the main shaft 1 within a sliding guide bushing 42 fixed to the wall of the main shaft 1, and has a mushroom-shaped head 43 housed within the tubular main shaft 1. is supported by a pressure cushion 15.

The arrangement of the shaft 41 and the direction in which the linear guide bearing 40 acts are as follows:
It is provided that the force generated by the pressure medium is opposed to the force 21 exerted on the roll member of the paper 20.

A new embodiment is shown in FIGS. 8 and 9.

This is similar to the previous embodiment, in which linear guide bearings 40 surround the two shafts.

However, the shaft 41 is supported by a ball bush 45.

However, the fundamental difference is that the shaft 41 does not support the pressure medium in a resilient pressure cushion, but the pressure medium acts directly on the end of the shaft 41.

Referring to FIG. 8, the shaft 41 is housed in an outer bushing 46 via a ball bushing 45.

The lower end opening of the bush 46 is closed by a roll membrane 47, which covers the unfixed end of the shaft 41.

The main shaft 1 is a receiving chamber for a pressure medium, which acts on the roll membrane 47, and the shaft 41 moves like a piston in the outer bush 46.

In FIG. 9, an O-ring 48 is attached to the end of the shaft 41, which provides an airtight connection between the shaft 41 and the outer bushing 46, so that the shaft 41 and the outer bushing 46 are airtight.
will maintain an operating relationship similar to that of a piston and cylinder.

The open lower end of the bushing 46 remains in contact with the pressure medium within the main shaft 1, so that the shaft 41 can move within the bushing 46.

Different configurations of linear guide bearings 50 are depicted in FIGS. 10 and 11.

This is fixed on the outside of the main axis 1, and the vertical bisector 1
The guide rail 51, which surrounds the guide rail 51 in a plane perpendicular to the bush 9, enters a gap in the ring bearing arrangement adjacent to the bush 9.

Guide rails 52 parallel to the guide rails 51 are fixed to both ends of the bushing 9, and both guide rails 51.
A bearing 52 provides a moving surface for the needle 53.

The needles 53 are arranged in parallel series in a retainer 54, which is well known for linear bearings, and the ring bearing arrangement 6 is moved axially by the bearing needles.

A bearing needle 55 is also arranged between the guide rail 52 and the main shaft 1.

As is clear from FIG. 11, the bearing needle 55 moves the ring bearing arrangement 6 radially in a direction opposite to the direction of action of the force 21 exerted by the paper 20.

As in the previous example, the force 21 exerted by the paper 20 on the wall of the main shaft 1
An opening 56 is provided on the side where the
6 is covered with a roll film 57.

A pressure medium contained within the main shaft 1 acts on this membrane 57 .

A piston 18 is mounted on the outer surface of the membrane 57, which piston 18 transfers the pressure from the pressure medium to the ring bearing arrangement 6.
The information is transmitted to Bush 9.

The reaction force 22 of the piston 18 and the acting force 21 due to the paper are equal and opposite to each other, and are kept in balance.

FIGS. 12 and 13 show an example in which the roll according to the present invention is used as a wide roll.

FIGS. 12 and 13 show that the roll sag to some extent when wide width work is required, and the roll sags due to the curvature in the running direction 80 of the paper 20.

As seen in FIG. 12, the paper 20 flows over a wide roll while maintaining a constant winding angle depending on the material. Since the paper 20 is to be fed at a certain angle with respect to the diagonal direction of the paper 20, as shown in FIG.

The width of the paper 20 increases as it passes through the wide roll.

An advantage of this embodiment is that when rolling a wide sheet of paper, force is evenly distributed over the entire width of the paper surface 20, so the tension on the paper surface 20 becomes uniform.

The paper is then fed in perfect condition and without wrinkles, resulting in a uniformly aligned paper roll.

This is extremely important.

Normally, the maximum gap between adjacent roller members 4 is about 1 mm.

However, when looking at the total width of the entire roller, its spread reaches 6 mm to 8 mm even under normal tension.

12 and 13, and in particular the embodiment of the roll without a cover 5, as seen on the right side of FIG. , the gap is 0.1 mrrr-0,
Since it is not 5mm L, the paper will not get caught in this gap when feeding the paper.

14 and 15 show an example in which the roller of the present invention is used as a load roller in a double roll winding device.

In this device, the sheet of paper 20 is wound onto a take-up roll 81 which rotates on support rolls 82 and 83.

The load roll presses the roll 81 from above.

A special feature of the pressurizing method using a pressure medium is that a uniform load is applied to the entire surface of the paper surface 20, so that a uniform, tightly wound cylindrical winding roll is produced.

[Brief explanation of drawings]

FIG. 1 shows a longitudinal sectional view of a roll according to the invention, and the guide in this part is a swivel bearing. FIG. 2 shows a cross-sectional view of FIG. 1 along the line II--II. FIG. 3 shows a partial cross-section of FIG. 2 along line III--III. 4 and 5 are the same longitudinal cross-sectional views as FIG. 1, but show different embodiments. FIG. 6 shows a longitudinal sectional view of a roll according to the invention. In this figure, the guide is designed as an auxiliary bearing. FIG. 7 shows a cross-sectional view of FIG. 6 taken along the line Vll-VII. FIGS. 8 and 9 are the same longitudinal cross-sectional views as FIG. 6, but show different embodiments. FIG. 10 shows a longitudinal section through an embodiment of a roller according to the invention, in which the guide is constructed as a straight guide bearing cooperating with a guide rail. FIG. 11 shows a cross-sectional view of FIG. 10 taken along line M-. FIG. 12 shows a side view of a wide roller as an application example of the roll according to the present invention. Figure 13 shows a view of the wide roller shown in Figure 12 from above. FIGS. 14 and 15 show, from the same side as FIGS. 4 and 5, an example of the application of the roll according to the invention as a riding roll in a paper winding device. DESCRIPTION OF SYMBOLS 1... Main shaft, 3... Frame, 4... Roll member, 6... Bearing device, 10.40.50.67... Linear guide device.

Claims (1)

[Scope of utility model registration request] A plurality of roll members 4 are loosely fitted to a main shaft 1 supported by a frame, and a bearing device 6 is interposed between the roll member 4 and the main shaft 1 to rotatably support the roll members 4. In the roller, the main shaft 1 is supported so as to be able to vibrate relative to the frame 3, the main shaft 1 is formed into a cylindrical shape, the inside thereof is used as a pressure medium storage chamber, and the bearing device 6 externally fitted on the main shaft 1 is used as a linear guide device. 10.40.50.67 allows the main shaft 1 to be displaced only in one direction in the radial direction, and each bearing device 6 is moved by the pressure of the pressure medium accommodated in the pressure medium storage chamber.
1. A roller that applies uniform pressure, characterized in that it is configured to press in the radial direction of a main shaft 1 and to evenly press each roll member 4 toward the side farther away from the main shaft.