FI116151B - Shoe press loading device - Google Patents

Description

BACKGROUND OF THE INVENTION The present invention relates to a shoe press loading unit according to the preamble of claim 1.

In paper machines, compression normally takes place in the press gap, i.e. the press nip between the press rolls, whereby the paper web is generally conveyed through the press nip between the water-absorbing press felts passing through the press nip together with the paper web. The length and geometric shape of the press nipple significantly influence the result of the press.

A highly effective elongated press nip is provided by a shoe press 15. The shoe press has a sliding or press shoe, which typically has a concave pressing surface. A concave pressing surface is provided against a counter member, such as a counter roll, and an endless belt runs between the slide shoe and the counter roll around the press shoe. The shoe press further includes a drive for pressing the sliding shoe against the counter roll.

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The shoe press drive unit is known to have a row of • · t hydraulic loading cylinders under the shoe. Typically, the press shoe should align with the surface of the backing roll and bend according to the deflection of the backing roll. The press shoe must also transmit the horizontal nip forces ·: ··· to the 25 shoe roll support structures. Typically, the press shoe will fit within the shoe age into the space shape provided by the loading cylinder below. track effectively.

On the other hand, the support structure beneath the load cylinder bends both in the machine MD 'and in the transverse CD direction, so that the support beam also • lies in the space.

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In the center of the machine, the distance between the press shoe and the support beam is different than in the periphery of the machine. As a result, »» »T: The opposite ends of the 35 load cylinders are constantly positioned in a different * space and the center region is stretched by deflection.

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FI 103591 discloses an arrangement for moving the shoe of a shoe press.

US 6083352 discloses another solution for loading and restoring a shoe press shoe 5. This load cylinder and subsequent tilt adjustment solutions for this type of cylinder are different options for eccentricity. In this solution, the cylinders are not very close to each other due to the clamping rims, so the load capacity per machine width ίο is not optimal.

The object of the present invention is to provide a novel solution for a shoe press loading unit which avoids the disadvantages of the prior art. Another object of the invention is to provide a shoe press loading unit which, e.g. the press distribution of the shoe press can be varied in many ways. In addition, the end of the shoe press loading cylinder on the press shoe side should be free-standing.

BRIEF DESCRIPTION OF THE INVENTION The apparatus according to the invention is characterized in that the second piston part and the cylinder part are pivotally connected to each other, preferably by pivot pins, so as to influence the tilting movement between the second piston part and the cylinder part ·: · *: 25.

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. * ··. The apparatus according to the invention is further characterized by what is stated in claims 2 to 10.

»·») !. V 30 The solution according to the invention has a number of significant advantages. In the solution according to the invention, the cylinders can be arranged almost interlocked, taking into account the necessary movements. The structural solution provides an entity that takes into account the transverse thermal expansion of the machine: X, as well as the alignment of the press shoe according to the shape of the • • * X I 35 caliper. By pivoting the cylinder part and the second piston part together, an advantageous solution is achieved which in part contributes to positioning the loading member in the desired manner. The direction of the joint can influence the direction of motion. The surface facing the inner wall of at least one piston member cylinder member is configured to allow tilting (angular offset 5) between the piston member and the cylinder member from the longitudinal direction of the cylinder member. This results in a loading member which allows the shoe press shoe part to be very well adapted to the desired conditions. Preferably, the desired tiltability is achieved, for example, by shaping the piston member at least partially spherically. An embodiment of the solution according to the invention comprises an auxiliary piston part for moving the load unit in the reverse direction relative to the compression direction.

The return-side system may be conveniently accomplished by varying the diameters pääkuormituksen enhancer, which can be achieved with respect to the normal load of about 15 l, l ... l, 3-fold loading.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will now be described in more detail by way of example 20, with reference to the accompanying drawing, in which

Fig. 1 is a cross-sectional view of a loading member according to the invention in the lower position, t 2 * Fig. 2 is a sectional view of a loading member according to the invention. : upright, • i »

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Fig. 3 is a cross-sectional view of a loading / unloading device according to the invention in the lowered position:

Fig. 4 is a cross-sectional view of the »load member with lifting / lifting device in the up position,

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Figure 5 illustrates the situation on the support beam with adjacent loading members

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35 the structure from which the upper parts have been removed, and

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Figure 6 is a side view of the load member cylinder.

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DETAILED DESCRIPTION OF THE INVENTION

The solution according to the invention is based on a system in which the loading member 5 consists essentially of three parts, two mutually piston pistons and a movable cylinder tube outside the pistons. The first piston 1, 35 rests freely on the press shoe 13 and the second piston 2, 67 rests on the support beam of the shoe press roll. Between adjacent pistons in the transverse direction of the machine, in the CD direction, there are separate T-rails, between which the pistons of the cylinders can be moved in the MD direction of the machine. The cylinder tube 3 is attached to the second piston 2 for pivoting.

The structural solution provides an assembly that effectively takes into account the transverse thermal expansion of the machine as well as the alignment of the press shoe with respect to the shape of the counter roll.

If the press shoe is loaded from top to bottom, a recovery mechanism is required to lift the press shoe. One embodiment of the solution 20 according to the invention comprises a separate hydraulic return to the first piston on the press shoe side.

• / In normal operation, the return hydraulics will have exactly the same pressure as the main load hydraulics, so that the return side will not resist the actual load in any way.

The return-side system may be conveniently accomplished by varying the diameters pääkuormituksen enhancer, which can be achieved with respect to the normal load of about l, l ... l, 3-fold loading. ·,: 30 This will release the back pressure from the return side during normal operation.

··· 'There is no pressure on the load side and only the reverse side is under pressure.

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The load-side pressure port is Cl and the reverse side of the pressure port C2, radio / •• .35 kenteessa in addition one or more of the ilmausyhde (not shown in the figures).

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Figures 1 and 2 show a shoe press shoe loading apparatus according to an embodiment of the invention. The first piston 1, in its portion against the inner surface of the cylinder space, is formed as a curved outer surface 5, preferably substantially a part of the spherical surface.

On the side surface 5, sealing means are provided for sealing the piston against the inner surface 9 of the cylinder 3. The sealing means comprise a seal groove 6 and a seal 7 provided in the groove, such as a sealing ring. The surface 10 facing away from the press shoe 13 of the first piston 1 has a preferably annular machining projection 8 having a thickness corresponding to the thickness of the lid 11 (Fig. 3).

The surface 12 of the first piston 1 is pressed against a press shoe, typically a surface 14 away from the nip of the press shoe 13 under load. The surface 12 of the compression shoe 13 of the first piston 1 has a substantially rectangular cross section, typically square. Hereby, the cross-sectional shape of the fastening heads of the piston parts differs from the cross-sectional shape of the part coming against the side surface of the cylinder part. The CD-directed surfaces 15, 16 of the machine have grooves 17, preferably T-key grooves, of the form-fitting member. The loading device 20 is movable in the longitudinal direction of the machine between the support beam and the press shoe.

The upper part of the first piston 1 also has T-groove machining 18 for the adjusting screw 19, as in Fig. 5. The upper part of the first piston 1 · · / 25 may additionally be provided with spaces for hydraulic inlet or outlet 26 ··: Figure 5 shows. One piston 2 has a spherical surface 21, a surface 21 having a seal groove 22 and a seal 23 which '** ·' seals to the inner surface 9 of the cylinder 3. The surface 24 of the second piston 2 is compressed. The surface 24 of the 30 is substantially square, and the CD-directed surfaces 27,28 of the machine have grooves 29, preferably T-key grooves, of the forming joint member. Another

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. ··. The MD-facing surfaces of the piston 2 are provided with spaces 30 for the lugs 31 of the cylinder 3. The surface 32 of the space 30 has recess machining and γ ·: threads 33 for the pivot pin 4. The surface 24 of the second piston 2 also has a load,. * 35 counter thread 100 for the metering hydraulics joint C3. An oval space 34 is machined for the support beam. Further, the outer surface of the second piston 2 has spaces for supplying or removing the hydraulics 26.

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In the situation of Fig. 2, the first piston 1 is in an upright position. The piston is then free to follow the movements of the shoe 13. The shoe 13 is supported on the CD-directional sides, whereby the inclination 5 of the cylinder 3 in the MD direction relative to the center of the spherical surface 21 is slight. As a result of the heat movement, the pistons 1 and 2 are disposed in different positions in the CD direction of the machine, whereby the inclination of the piston 3 with respect to the center of the sphere 21 in the CD direction is wide. The structure allows the trajectory needed by the whole.

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Figure 3 shows another embodiment of the apparatus according to the invention. Therein, the first piston 35 is substantially similar to the first piston 1 in Figures 1 and 2. A surface 11 away from the press shoe of the first piston 35 is provided with a lid 15 by fastening means 37. The first piston 35 has threaded holes 38 and channel bores 41 for C2. The plunger 35 further has a plurality of expressions not shown in the figure. Cover 11 has recesses 42 and bores 43 for fastening members 37. In addition, cover 11 has seals 44,46 and guide ring 48 and corresponding grooves 45,47,49. Inside the first piston 35 are machined spaces SI and S2. The guide ring 50 of the cover 11 partially submerges in the space SI, thereby centering the cover 11 concentric with the first piston 35. Within the space SI is a plunger 51 which is movable relative to the first plunger / cylinder 35 as the plunger 35 rises or lowers. The second piston 51 has a seal 52 and a guide ring 53 and their respective grooves 54.55. The auxiliary piston 51 is sealed and guided externally to the outer surface of the space SI. The stem 57 of the auxiliary piston 51 comprises one or more:. As the first piston 35 rises or lowers, the pressure medium flows from space S3 through channels 58 and 56 to space S2, whereby conditions S2 and S3 are at the same pressure. The lid 11 is sealed on its surface 59 against the surface 36 of the piston 35 as well as on its inner surface 60 against the outer surface of the piston rod 57. The auxiliary piston 51 remains substantially stationary as the lid 11 moves up and down with the piston 35. The piston rod 57, the first piston 35, the auxiliary piston 51 and the lid 11 delimit the space SI into which a pressure medium, such as an oil, is conveyed together through C2. In normal driving, space SI is at the same pressure as spaces S3 and S2, but space SI can also be left at 0, whereby the effect of the pressure on the first piston 35 is greatly enhanced. By choosing the right diameter ratios, you can always achieve a 30% boost compared to a simple pressure effect. The piston rod 57 is tapered at one end by one or more axial steps 61.62.

5 At one end of the piston rod 57, there is a bolt thread 63 into which a lock nut 66 locks the ball bearing 64 between a single stepped shoulder blade and a washer 65.

The second piston 67 is substantially similar to the second piston 2 in Figs. 1 and 2. The second piston 67 has a machined space S4 on the surface 68 of the piston 51 so that the arm 57 can pivot about the center of the ball bearing 64. The space S4 is machined to the space S6 by cylindrical or conical machining, the space S5, within which the extension 61 of the piston rod 57 can move and rotate freely. The space S6 for the ball bearing 64 is partially pressed into the piston 67 and the sleeve 69. During loading, the ball bearing 64 can move freely in unloaded state S6. Inside the sleeve 69 is a machining space S7 for a washer 65, a lock nut 66 and a bolt-thread 63. The pressurized medium is conveyed from the space S7 through the one or more groove machining units 70 to the space S6 in the loading condition and in the recovery phase. From space S6, the pressure medium flows into space S4 and further into space S3 through space S5 and one or more channel bores 71. The sleeve 69 and the piston 67 are connected by means of fastening means 72. The sleeve 69 has recesses 73 and bores 74 for fastening means 72. .... The piston 67 has threaded bores 75 for the fastening members 72. The outer * 25 surface 76 of the sleeve 69 is centered relative to the center of the piston 67 from the inner surface of the piston 77.

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The outer diameter of the sleeve 69 is reduced by one or more steps 78. The sleeve 69 has a seal 79 and a corresponding groove 80. The sleeve 69 engages and seals on its surface 81 to the inner surface of the piston 82. The sleeve 69 has a counter thread 83 on its face 84. 30 to engage the lock nut 66. In addition, hol: · · · · · · · · · · · · · · · · · · · · · The cat 69 may have one or more phrases that are not shown in the figure. The center of the radius of the spherical outer surface of the piston 67 is aligned with the center of the ball bearing 64 P1.

·; '35 Under normal conditions, conditions S1-S7 have the same pressure: whereby the terminals C1 and C2 are connected to an external system such that; v. pressures and volumetric flows in different states correspond to the desired operating conditions. The state S2 expands to the SI side of the state and correspondingly the SI state decreases to almost its minimum value. Correspondingly, the volume of the space S3 increases with the traveling distances. If it is desired to increase the pressure effect on the shoe, the pressure is removed from the space S1, whereby the pressure effect on the surface 14 of the press shoe 13 is rigid.

In Fig. 5, there are rows of load units on top of the support beam, of which two to the right are the basic structures without the effect of removal and restoration. The left-hand loading unit is equipped with an auxiliary piston. Overhead sections have been removed from the loading units and only a portion is visible. One of the pistons 2 is substantially square, as is the other piston 67. In the sleeve 69 inside the piston 67, the surface 78 is partially bevelled 85. The CD-directed sides of the surface 78 of the sleeve 69 are machined straight 86.88. The support beam surface 25 is machined with MD grooves 90 whose surfaces 87 and 89 correspond to the surfaces of sleeve 69 86.88. The second pistons 67 and 2 can be moved in the MD direction of the machine for a desired distance, as well as the first pistons 35 and 1 (not shown).

In Fig. 6, the clearances 91 and 93 around the pivot pin 4 of the cylinder 3 allow the cylinder to rotate slightly around the point P1 in the MD direction of the machine. The clearances 93 and 94 allow the cylinder 3 to rotate about a point P1 in the CD direction of the machine due to thermal expansion, whereby the pistons 1 and 2 and 35 and 67 move relative to each other. Cylinder 3 can '. 25 may also be secured to the second piston 2, 67 by one or more compression / tension springs (not shown) which are an alternative mounting arrangement for the pins 4.

It will be apparent to one skilled in the art that the invention is not limited to the embodiments set forth above, but may be varied within the scope of the appended claims. Depending on the embodiment, the features that may be presented in the specification together with other features may also be used separately.

Claims (11)

116151 A shoe press loading unit specifically designed to load a shoe press shoe, the unit comprising at least one cylinder part (3) and a first piston part (1, 35) and a second piston part (2, 67) arranged in the cylinder part, wherein at least one piston part (1, 2, 35, 67) the surface (5, 21) facing the inner wall (9) of the cylinder member (3) is shaped to allow tilting (angular misalignment) between the piston member (1, 2, 35, 67) and the cylinder member (3). From the direction, characterized in that the second piston part (2, 67) and the cylinder part are pivotally attached to each other, preferably by the pivot pins (4), so as to influence the tilting movement between the second piston part and the cylinder part. Load unit according to Claim 1, characterized in that the cylinder part (3) is arranged on the second piston part (2, 67) pivotally pivotally with respect to the longitudinal axis, preferably with pivot pins (4). Load unit according to claim 1 or 2, characterized in that the first piston part (1, 35) is arranged on the shoe press shoe (13) and the second piston part (2, 67) is arranged on the shoe press support beam (25). • · · Load unit according to one of Claims 1 to 3, characterized in that at least a portion of the first and / or second piston • *: '* i part (1, 2, 35, 67) of the inner wall (9) of the cylinder (3). the facing surface (5, 21) being at least partially spherical. S '·': 30 Load unit according to one of Claims 2 to 4, characterized in that the cylinders (3) and the pivot pin (4) are spaced (91, 92, 93, 94). »» I Load unit according to one of Claims 1 to 5, characterized in that the unit comprises an auxiliary piston part (51). I · I * t »I I I t ίο 116151 A loading unit according to any one of claims 1 to 6, characterized in that the auxiliary piston part (51) is arranged in the second piston part (67) such that the auxiliary piston stays substantially stationary with the second piston and the auxiliary piston part extends into that the auxiliary piston (51) and / or the first piston part (35) can move relative to one another. Load unit according to one of Claims 1 to 7, characterized in that at least one first piston part (1, 35) and / or one second piston part (2, 67) is provided with means for movably arranging the load member and / or press shoe in the longitudinal direction (MD). . Load unit according to one of Claims 1 to 8, characterized in that at least one of the piston portions (1, 2, 35, 67) has grooves for movably arranging the load unit between the support beam and the press shoe. Load unit according to one of Claims 1 to 9, characterized in that the piston part of the auxiliary piston (51) is arranged in a cylinder space formed in the first piston part (35). • t • 1 · • · · t · · »» • »t i t 11 116151