Patent Publication Number: US-7582192-B2

Title: Loading device for a shoe press

Description:
BACKGROUND OF THE INVENTION 
   The present invention relates to a loading unit for a shoe press. 
   In paper machines, the pressing normally takes place in a press nip between press rollers, the paper web being generally passed through the press nip between water-absorbing press felts which run through the press nip together with the paper web. The length and geometric shape of the press nip have a significant effect on the pressing result. 
   A very efficient extended press nip is achieved by using a shoe press. The shoe press comprises a slide or press shoe, which typically has a concave pressing surface. The concave pressing surface is arranged against a backing element, such as a backing roll, and an endless belt runs between the slide shoe and the backing roll. In addition, the shoe press comprises an actuating device which presses the slide shoe against the backing roll. 
   As is known, the actuating device of the shoe press has a row of hydraulic loading cylinders under the show. Typically, the press shoe must be set according to the surface of the backing roll and bend according to the curvature of the backing roll surface. The press shoe must also transmit the horizontal nip forces to the supporting structures of the shoe roll. The press shoe typically assumes inside the shoe roll a spatial shape that the loading cylinder under it has to effectively follow. 
   On the other hand, the supporting structure under the loading cylinder bends both in the longitudinal direction MD and in the transverse direction CD of the machine, so that the supporting beam also assumes a spatial position. 
   In the middle part of the machine the distance between the press shoe and the supporting beam is different than in the edge areas of the machine. As a result of the overall arrangement, the opposite ends of the loading cylinder continuously assume different spatial positions and the middle part is stretched due to the deflections. 
   Patent specification FI 103591 discloses an arrangement for moving the shoe of a shoe press. WO 01/98584 discloses another arrangement in an extended nip press for a paper or board machine. 
   Patent specification U.S. Pat. No. 6,083,352 discloses another approach to the loading and pull-back of the shoe of a shoe press. Solutions based on adjustment of the loading cylinder and later solutions based on adjustment of tilt for this type of cylinder are different alternatives of eccentricity. In the solution in question, the cylinders can not be mounted very close to each other due to the fastening clamps, so the loading capacity per meter of machine width is not the best possible. 
   Specification EP 737776 discloses a solution wherein the frame of the shoe roll contains a machined space for a loading element. A piston is fixed to the bottom of the machined space. A cylinder moves on the piston. The cylinder is continuously urged by a spring against the shoe part. The pressure inside the piston and cylinder produces the actual loading pressure. The shoe part can move in relation to the pistons. The cylinder can turn in relation to the piston. 
   Specification U.S. Pat. No. 5,935,385 discloses a corresponding structure in which the cylinder can move into the frame of the shoe roll in the machined space. 
   Specification EP 74+0016 further discloses a simple approach to solving the problem in question. In this case, the frame of the shoe roll forms a cylinder block in which the pistons are movably mounted. The upper end of the pistons leans against the loading shoe of the shoe roll, and the loading shoe can move freely in relation to the cylinder. The piston is held against the bottom of the loading shoe by means of a spring. 
   In specification U.S. Pat. No. 6,093,283 the piston is fixedly fastened either to the loading shoe or to the frame of the shoe roll and correspondingly the cylinder can move in relation to the piston and shoe roll or the loading shoe. 
   A problem with all the prior-art solutions is that they provide only limited possibilities of adjustment. In addition, to make an adjustment, it has been necessary to dismantle the whole shoe press structure and only then carry out the adjustment. 
   SUMMARY AND OBJECTS OF THE INVENTION 
   The object of the present invention is to achieve a completely new type of solution for the loading unit of a shoe press that will allow the drawbacks of prior art to be avoided. Another object of the invention is to achieve a shoe press loading unit that will make it possible e.g. to vary the distribution of compression of the shoe press in a versatile manner. A further object of the invention is to achieve an adjustment solution that can be used without dismantling the structure of the shoe press. 
   The solution of the invention has numerous significant advantages. The pressure distribution or “tilt” prevailing in the press nip can be adjusted by the solution of the invention in a single row solution from outside the machine or alternatively in a solution of more economical cost also from inside the machine in a very simple manner. The solution allows an adjustment to be made without dismantling the structures of the machine. The adjustment can be easily automated. 
   At the same time, we have also taken into account the possibility of turning the roll upside down independently of the loading direction. This allows, among other things, the loading unit to be pulled back from the pressing position by means of a second cylinder-piston unit. The second cylinder-piston unit can be used to enhance the compression achieved by the loading unit. The structural solution provides an overall arrangement in which the transverse thermal expansion of the machine is effectively taken into account while ensuring that the press shoe is set according to the shape of the backing roll. In addition, by using a second cylinder-piston unit disposed inside the loading unit, a solution of compact structure for the pull-back of the loading unit is achieved. The solution of the invention also ensures that the adjusting elements are locked in a loading situation when the loading unit is at least partially supported against the adjusting elements. 
   Further scope of applicability of the present invention will become apparent from the detailed description given hereinafter. However, it should be understood that the detailed description and specific examples, while indicating preferred embodiments of the invention, are given by way of illustration only, since various changes and modifications within the spirit and scope of the invention will become apparent to those skilled in the art from this detailed description. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The present invention will become more fully understood from the detailed description given hereinbelow and the accompanying drawings which are given by way of illustration only, and thus are not limitative of the present invention, and wherein: 
       FIG. 1  presents a cross-sectional view of a loading device according to the invention in a low position, 
       FIG. 2  presents a cross-sectional view of an embodiment of the locking device of the invention in a low position, 
       FIG. 3  presents a cross-sectional view of a loading device according to the invention in a high position, 
       FIG. 4  presents a cross-sectional view of a loading device provided with a releasing/lifting device in a low position, 
       FIG. 5  presents a cross-sectional view of a loading device provided with a releasing/lifting device in a high position, 
       FIG. 6  illustrates the fastening of loading device provided with a releasing/lifting device on the surface of a supporting beam, in cross-section along line A-A in  FIG. 5 , 
       FIG. 7  illustrates the fastening of the loading device provided with a releasing/lifting device below the shoe, in cross-sectional view along line B-B in  FIG. 5 , 
       FIG. 8  presents a second embodiment of the solution of the invention, 
       FIG. 9   a ) presents a detail of  FIG. 8  in the form of a section C-C, 
       FIG. 9   b ) presents an adjusting ring, 
       FIG. 10  presents a detail of a loading device provided with a releasing/lifting device according to the second embodiment along line D-D in  FIG. 11 , 
       FIG. 11  presents another embodiment of the loading device provided with a releasing/lifting device, 
       FIG. 12  presents the loading device sectioned along line E-E in  FIG. 11 , 
       FIG. 13   a ) and  13   b ) present a loading shoe in side view, as seen from the direction of the machine MD, 
       FIG. 14   a ) and  14   b ) present a detail of an embodiment of the loading cylinder in different positions inside the shoe beam, 
       FIG. 15   a ) and  15   b ) present a detail of another embodiment of the loading cylinder in different positions inside the shoe beam, 
       FIG. 16  presents an embodiment of the apparatus of the invention, 
       FIG. 17  presents another embodiment of the apparatus of the invention, 
       FIG. 18  presents the apparatus of the invention as seen along line F-F in  FIG. 16 , 
       FIG. 19  presents the apparatus of the invention as seen along line G-G in  FIG. 17 , 
       FIG. 20  presents the apparatus of the invention as seen along line H-H in  FIG. 12 , 
       FIG. 21  presents a diagram of an arrangement for controlling the apparatus of the invention, and 
       FIG. 22  presents a diagram of an arrangement for controlling the apparatus of the invention. 
   

   DETAILED DESCRIPTION OF THE INVENTION 
   The loading unit of the shoe press is especially designed to apply a load to the press shoe or press beam  70  of the shoe press (hereinafter referred to as press shoe  70 ). The unit comprises a first cylinder part  6 ,  71 , a first piston part  1 ,  114  disposed in the cylinder part, the outer surface  2  of which piston part facing towards the inner wall of the cylinder part is so shaped as to permit mutual tilting of the piston part and cylinder part. The piston part  1  and/or the cylinder part  6  are/is provided with means for arranging a loading element K and/or a press shoe  70  to be movable in the longitudinal direction MD of the machine, and the piston part  1  and/or the cylinder part are/is provided with a flow path  22  for reducing lateral forces between the loading element and the shoe press supporting beam  12  or equivalent. 
   The loading element K is at least partially supported at least at one end, either on the side of the press shoe  70  or on the side of the supporting beam  12 , on transfer means  225 ,  226 ,  185 . 
   According to a preferred embodiment, the loading element K is at least partially supported at least at one end, either on the side of the press shoe  70  or on the side of the supporting beam  12 , on the transfer means in such manner that the transfer means  225 ,  226 ,  185  are locked at least when the compressive action of the loading unit is on. 
   In the embodiment presented in  FIG. 4 , the loading element K contains a second cylinder-piston unit  86 ,  100 ,  105  arranged inside it. 
   The cylinder part  86  of the second cylinder-piston unit is so arranged in the first cylinder part  71  that it extends into the chamber space S between the first cylinder part  71  and the first piston part  86 . 
   The piston rod  105  of the piston part  100  of the second cylinder-piston unit is arranged, preferably by the opposite end relative to the second piston part  100 , in the first piston part  114 . In the embodiment illustrated in  FIG. 4 , the piston rod  100  of the second cylinder-piston unit is arranged in the first piston part  114  in a manner permitting motion and/or tilting. The piston rod  100  of the second cylinder-piston unit is arranged in the first piston part  114  with a joint  113  that preferably comprises a spherical surface part. 
   The loading element K further comprises at least one flow path  22  from the chamber space S between the first cylinder part  6 ,  71  and the first piston part  1 ,  114  to the space between the loading element K and the supporting surface, such as the supporting beam  12 . This can be utilized to reduce the lateral forces. 
   Arranged in the loading element K is at least one first flow path  116  for conveying a pressure medium into the chamber space S between the first piston and the first cylinder. The apparatus comprises at least one flow path  196 ,  107  into a first chamber space S 3  between the second cylinder space and the second piston. 
   The apparatus comprises a flow path  130 ,  131 ,  132  into a second chamber space S 2  between the second cylinder space and the second piston, said chamber space being located on the side of the piston rod  105 . 
   The shoe press comprises a number of adjacent loading elements K acting on the press shoe  70 , the first end of said elements being supported on the supporting beam  12  of the shoe press while the second end meets the press shoe  70 . The loading elements K are moved in the machine direction MD in the space between the press shoe  70  and the supporting beam  12  by acting on the loading element K at least at the end adjacent to the press shoe in such manner that the end adjacent to the press shoe is moved in the machine direction MD in relation to the press shoe  70  and that the end of the loading element adjacent to the supporting beam  12  can be caused to freely assume a position in relation to the supporting beam  12 , preferably at least during the transfer. The loading element K is acted on directly or via a transmission. According to a preferred embodiment, the loading element is acted on by at least one transfer element, most suitably a bar element  225 ,  226 , which is moved in the transverse direction CD of the machine. According to a second embodiment, the loading element K is acted on via a transmission, wherein an eccentric element acts on the loading element while the eccentric element is acted on by a bar element. According to a further embodiment of the invention, the loading element is acted on by an eccentric toothed gear  186 , which is rotated by a toothed bar element  185 . According to an embodiment, a projection part  28  formed at the end of the loading element K adjacent to the press shoe is moved between guide surfaces  31 ,  32  extending in the machine direction MD, while the transfer elements acting in the transverse direction of the machine produce a transfer movement in the machine direction MD. According to an embodiment, a pressure medium is supplied into the space between the supporting beam  12  and the end of the loading element K adjacent to the supporting beam to reduce lateral forces. 
   One embodiment allows adjustment of the distribution of loading pressure during operation of the machine. In this case, the distribution of loading pressure can be adjusted continuously on the basis of measurement data. 
   The press shoe  70  is acted on by the loading unit K, which comprises a cylinder-piston unit. This will be dealt with in more detail later on. 
   The shoe press comprises a number of adjacent loading elements acting on the press shoe  70 , the first end of said elements being supported on the supporting beam  12  of the shoe press while the second end meets the press shoe  70 . The apparatus comprises means for moving at least the end of the loading element K adjacent to the press shoe  70  in the machine direction MD, and means for reducing lateral forces between the supporting beam and the loading element end adjacent to the supporting beam  12 . According to an embodiment, the means for moving at least the end of the loading element K adjacent to the press shoe  70  comprise at least one transfer element  225 ,  226 ,  185  arranged in conjunction with the press shoe  70 , which transfer element is movable in the transverse direction of the machine and by means of which a backing element  28  of the loading element K is moved directly and/or via a transmission mechanism. Arranged in conjunction with the press shoe  70  are guide surfaces  31 ,  32  or guide elements for guiding the motion of the loading element, especially to make it move in the machine direction MD. The transfer element  225 ,  226  is provided with a guide surface  227 ,  228 ;  235 ,  236  and the loading element is provided with a mating surface  229 ,  230 ,  161  so that the guide surface moves the loading element by the mating surface. The transfer means moving the loading element K typically comprise actuating devices arranged in or near the end area of the press shoe  70 . The loading element K is usually a cylinder-piston combination. This embodiment will be described hereinafter in greater detail. 
   In one embodiment, the transfer means comprise two bar elements  225 ,  226 , which together influence the position of the loading element in the machine direction MD. In another embodiment, the transfer means consist of an eccentric wheel, such as an eccentric toothed gear  186 , which is driven by a toothed bar element  185  connected to the actuating devices. 
   The means for reducing the lateral forces between the supporting beam and the loading element end adjacent to the supporting beam comprise at least one conduit for conveying a pressure medium into the space between the supporting beam and the loading element 
   The adjusting devices are preferably arranged in a space formed in the press shoe. In a loading situation, the loading element K locks the adjusting elements, which typically according to the invention are located between the loading element K and the press shoe  70 , in place. Some embodiments of solutions according to the invention are further described in greater detail in the following. 
   In  FIG. 1 , the piston  1  has an outer surface  2  of a curved shape in the portion placed against the inner surface of the cylinder space, preferably a substantially spherical shape, i.e. forming part of a spherical surface. Provided on the outer surface  2  are sealing means for sealing the piston against the inner surface  5  of the cylinder  6 . The sealing means comprise a sealing groove  3  and a seal  4  arranged in the groove. The piston  1  has a recessed outer surface. Due to the difference between the outer surface  7  of the recessed part of the piston and the outer surface  2  facing against the inner surface  5  of the cylinder, there is formed between the inner surface of the cylinder and the outer surface of the piston a space  8  that enables the cylinder  6  to turn about point X 1 . Point X 1  is typically at the center of surface  2 . Placed between the piston  1  and the cylinder  6 , typically in the chamber space S between them, is a pre-loading element, such as a spring  9  which causes the outer surface  10  of the piston  1  to be pressed against the surface  11  of the supporting beam  12 . Correspondingly, the spring  9  presses the surface  15  of the cylinder  6  as the surface  16  of the loading shoe. Depending on the direction of the loading, the spring  9  is not necessarily needed. The spring is tensioned against surface  17  of the cylinder  6  and surface  18  of the piston  1 . 
   The piston  1  has a flange  19  at the end adjacent to the supporting beam  12 . Inside the flange  19 , on surface  10 , is a groove  20  for a seal  13 . In addition, surface  10  is provided with a groove  21  for a seal  14 . A pre-loading element, typically a spring  9 , simultaneously precompresses the seals  13  and  14  placed between the piston and the supporting beam. The diameter of seal  13  is chosen specifically for each case. If the main load pressure p 1  applied via conduit C 1  is to be used to load surface  10  against surface  11 , then a seal  13  having a diameter smaller than the diameter of cylindrical surface  5  is selected. The diameter of seal  13  can also be so chosen that oil will leak through between surfaces  10  and  11 . In this case, as compared to pressure p 1 , a balanced pressure p 3  corresponding to a leakage will be set up between seals  14  and  13 . 
   The loading unit is provided with flow channels for a pressure medium. From surface  18  of the piston  1 , one or more holes  22 , preferably threaded holes, have been made to surface  10 , typically by drilling. Mounted in the flow path  22  with threaded holes are nozzle pieces  23 . The nozzle pieces  23  may be provided with a back-pressure valve to prevent flow from surface  10  into the space inside the piston  1 . The pressure medium, such as oil, flows from inside the piston  1  via the nozzle pieces  23  into the space between surfaces  10  and  11 . The aperture inside the nozzle  23  is varied to achieve a desired flow rate. 
   The diameter of the outer surface  24  of the cylinder  6  is substantially equal to the diameter of the outer surface  25  the piston  1 . In the low position, surface  26  of the piston  1  touches surface  27  of the cylinder. 
   On the surface  15  of the cylinder  6  adjacent to the loading shoe is a guide element, such as a projection  28 , see also  FIG. 7 . Formed in the projection is at least one guide surface, typically two guide surfaces. In the figure, the guide surfaces consist of two sides  29  and  30 , which have been machined to make them straight and which, in an operating situation, extend in the direction of the MD axis of the machine. Surfaces  29  and  30  are in contact with the walls  31  and  32  of the groove inside the loading shoe. 
   Guided by the projection  28 , the cylinder  6  can move in the MD direction of the machine in the groove of the loading shoe through a distance of ±Δa in relation to the basic center line CL 1  of the cylinder. 
   The piston  1  follows the motion of the cylinder  6  in the machine direction MD. The cylinder  6  can be moved when it is in the low position, but the structure can also be adjusted in the operating state of the machine, depending on the selected mode of control/adjustment. Seal  14  may be of a type capable of bi-directional sealing with different pressures inside and outside, and likewise seal  13 . 
   During movement of the cylinder  6 , the piston  1  can be assisted by a separate pressure p 3 . The pressure p 3  is supplied via a conduit C 3  into a manifold  33  and further through a channel bore  34  into the space between surfaces  10  and  11 . The action of the pressure will now be applied to the area between the seals  13  and  14 , and it can be partly discharged via the nozzles  23  into the space S defined by the inner surfaces of the cylinder  6  and piston  1 . 
   When the cylinder is in the low position, the pressure p 1  in space S is 0 and the overpressure is discharged through conduit C 1  into the tank. Alternatively, when the nozzle  23  contains a back pressure valve, pressure p 3  can not be discharged into cylinder  1 . The conduit C 1  is connected to a manifold  35 . In an operating situation, the pressure p 1  is conveyed from the manifold  35  through a channel  36  into space S 1 . 
   Between surfaces  18  and  10  of the piston  1  is a channel bore  37  through which the pressure p 1  can be discharged from space S 1  into space S. In an operating situation, the cylinder  6  and the piston  1  move further apart from each other and assume spatial positions relative to each other. 
   The arrangement may comprise one or more conduits C 1  and C 3 , and likewise one or more manifolds  33  and  35 , e.g. according to zone divisions. The manifolds may be welded onto the supporting beam of the shoe roll in a pressure-tight manner. Space S 1  may be of an oval shape or a round machined space that permits the piston  1  to move in the machine direction MD. The manifold  35 , 33  has a counter-thread  46 , 48  for the pressure conduit C 1  and C 2 . The main channel  47 , 49  is inside the manifold  35 , 33 . Distribution channels  36 , 34  start from the main channels  47 , 49 . The conduits C 1  and C 3  are connected to an external oil supply system, or to a corresponding pressures system (not shown in the figure). The ends of the distribution channels  33 , 35  are plugged with a separate piece (not shown in the figure), to the extent necessary because of flushing and inspection requirements. In an operating situation, the flow through conduit C 3  into the tank is closed and pressure p 3  follows pressure p 1 . 
     FIG. 2  illustrates a situation where the shape of the supporting beam  12  of the shoe roll differs that of the supporting beam in  FIG. 1 . Typically, the supporting beam in  FIG. 2  is made by casting or forging. In this case, the manifolds  40  and  41  are secured to the shank portion of the supporting beam  12 . The manifolds  40  and  41  are divided into sections, e.g. according to zone adjustment. The number of oil supply conduits C 1  and C 3  is one or more, and likewise that of manifolds  40 , 41 . The supporting beam  12  is provided with counter-threads  42 ,  42  for the manifold fixing bolts  44 ,  45 . The manifolds  40  and  41  are provided with counter-threads  48  and  46  for the conduits C 3 , C 1 . The manifolds  40  and  41  contain the main channels  47 ,  49  for pressures p 1  and p 3 . Provided in the manifolds  40  and  41  are machined counter-sunk holes  51 ,  50  and clearance holes for the securing screws  44 ,  45 . The main channels  47 ,  49  are connected via channel bores  54 ,  55  to the channel bores  56 ,  57  in the supporting beam. The manifolds  41 ,  40  are sealed by surfaces  58 ,  60  to the surfaces  59 ,  61  of the supporting beam  12 . 
   Placed between the supporting beam  12  and manifolds  40  and  41  are seals  62 ,  64 , and the manifolds  40  and  41  are provided with sealing grooves  63 ,  65  corresponding to the seals  62 ,  64  around the bores  54 ,  55 . From manifold  40 , pressure p 3  is conveyed via main channel  49  via bores  55 ,  57 ,  34  into the annular space between the seals  13  and  14 . From manifold  41 , pressure p 1  is conveyed from main channel  47  via bores  54 ,  56 ,  36  into space S 1  and further via bore  37  into space S. Depending on the load situation, the cylinder  6  and the piston  1  additionally have air conduit bores not shown in the figure. Oil supply into channels  56 , 57  can also be implemented using only a pipe structure without a separate distribution channel. In this case, channel portions  56 , 57  are provided with inner threads and a separate coupling part for attaching the oil supply pipe to the channel is secured to each thread. According to the zone division, the main oil pipe is divided by means of a T-coupling into lateral branches and further to the couplers of channels  56 , 57 . 
     FIG. 3  illustrates a situation where the loading element according to  FIG. 1  is in the high position. The cylinder  6  has risen to its maximum position in relation to the piston  1 . In this situation,
         the cylinder can freely follow the movements of the press shoe  70     the press shoe  70  is supported from the sides oriented in the CD direction, so there occurs but little tilting of the cylinder  6  in the MD direction in relation to the center X 1  of the spherical surface  2     due to thermal motion and loading, the cylinders  6  follow the motion of the press shoe  70 , so there occurs more extensive tilting of the cylinders  6  in the CD direction in relation to the center of the outer surface  2  than in the MD direction.   on the other hand, the pistons  1  can follow the motion of the cylinders in the CD direction of the machine, especially if there is a pressurized sliding film layer between the supporting beam  12  and the pistons  1 .       
     FIG. 4  presents a second embodiment of the loading device of the invention. The solution according to the second embodiment comprises a release/lifting cylinder. Cylinder  71  contains another cylinder tube  86  inside it. A cover  88  is fastened onto cylinder  86  by means of fastening elements  89 . Threaded holes  90  for the fastening elements  89  are provided in the surface  87  of the cylinder. The cover  88  is provided with machined counter-sunk holes  91  and clearance holes  92  for the fastening elements  89 . Machined inside the cylinder  86  is a space S 2 , into which a guide ring of the cover  88  partly sinks and at the same time centers the cover  88  with the cylinder tube  86 . The guide ring  93  together with surface  87  and the machined space S 2  inside the cylinder  86  forms a space  94  in which a seal  95  is fitted. The cover  88  is provided with a seal  96  and a guide ring  97  and corresponding grooves  98 ,  99 . Inside the cylinder  86  is a piston  100 , which remains substantially immovable as cylinder  86  is moving in step with cylinder  72 . The piston  100  is provided with a seal  101  and a guide ring  102  and corresponding grooves  103 ,  104 . The piston  100  is guided and sealed by its outer surface according to the outer surface of space S 2 . In addition, the cylinder  86  contains a space S 3  above the piston. The piston rod  105  contains one or more channel bores  106 ,  107 . When the cylinder  86  moves upwards or downwards, oil will flow from space S 4  via the channels  106 ,  107  into space S 3 , so the pressure in spaces S 4  and S 3  is the same. The cover is sealed by its surface  108  against surface  87  of the cylinder  86 , and likewise by its inner surface  109  against the outer surface of the piston rod  105 . The piston  100  and the piston rod  105  remain substantially immovable as the cover  88  is moving upwards and down-wards with the cylinder  86 . The piston rod  105 , the guide part  93  of the cover  88 , the piston  100  and the inner surface of cylinder  86  define a space S 2  into which oil is supplied via conduit C 2 . See  FIGS. 5 and 7 . 
   In normal operation, space S 2  is at the same pressure with spaces S 3 , S 4 . The piston rod  105  is narrowed at one end by one or more axial indentations  110 . One end of the piston rod  105  is provided with a bolt thread  111  for a lock nut  112  to be screwed onto it to lock the spherical bearing  113  against the axial shoulder. Piston  114  is in principle similar to piston  1 . Machined in surface  115  of the piston is a cylindrical space S 5 . From space  55  there is a bore  37  corresponding to that in piston  1 . The piston rod  105  and bore  37  define space S 4 . From space S 5  one or more channel bores  116  lead to the space inside the piston  114 . The supporting beam  12  is provided with a cylindrical machined counterboring S 6  for a lock nut  112  corresponding to space S 5 . The spherical bearing  113  can slide in space S 5  according to cylinder  86  and  71 , as well as turn in step with cylinder  86  and  71 . In normal operation, the spherical bearing  113  and the piston as well as the piston rod  105  are in an unloaded state as pressure p 1  prevails everywhere inside the structure. In an operating situation, the pressure p 1  conveyed via conduit C 1  into the main channel  47  and further through bore  36  into space S 6 , which communicates with space S 5 . From space  55 , the pressure p 1  is conveyed via bores  116  into the space inside piston  114 . Inside the piston, the oil is conveyed into space S 4  and further via channels  106  and  107  into space  53 . 
   In the operating situation, the pressure p 2  in space S 2  is the same as pressure p 1 . The outer surface  117  of piston  114  is provided with a groove  118  which can receive the projection  120  of a bracket  119  as the piston  114  is moving on the supporting beam  12 . 
   The bracket  120  is provided with machined counterborings  121  and clearance holes  122  for a fastening element  123 . The supporting beam  12  is provided with threaded holes  124  for the fastening element  123 . The bracket  120  is fastened to the supporting beam  12  by means of the fastening element  20   123 . The piston  114  is movably mounted on the surface of the supporting beam, with the flange remaining under the bracket  120  and the projection  119 . In a releasing and lifting situation, the cylinder  71  is held fast on the press shoe  70  and correspondingly the piston  114  is held fast on the supporting beam  12 . Due to the action of pressure p 2  in space S 2  when the press shoe  70  is upside down, the loading shoe rises upwards. 
   The outer surface  72  of cylinder  71  is provided with an annular groove  73  into which the projection  75  of a holding block  74  is set. See also  FIG. 7 . Arranged radially in the holding block  74  are counterborings  77  and clearance holes  78  for fastening screws  76 . Arranged radially in the cylinder  71  are mating threads  79  for the fastening screws  76 . In the area of the fastening screws  76 , the bracket  75  is notched as far as necessary. Holding block  80  is provided with machined counterborings  81  and clearance holes  83  for securing bolts  82 . The press shoe  70  is provided with corresponding threaded holes  84  for the securing bolts  82 . Holding block  80  has a machined space  85  for the fastening part  74 . The cylinder  71  is secured to the surface  16  of the loading shoe by means of fastening elements  74 ,  80  and fastening screws  76 ,  82 . The cylinder  71  can move in the machine direction MD in relation to the press shoe  70 , the holding blocks  74 ,  80  are so designed as to permit movement in the MD direction. The parts  74 ,  80  are so designed as to allow some movement of the cylinder  71  in the CD direction of the machine, too. 
   In  FIG. 5 , the cylinder  86 ,  71  has channel bores  130 ,  131 ,  132  inside it. Via conduit C 2 , a pressure p 2  is conveyed into space S 2  through the channels  130 ,  131 ,  132 . Cylinder  86  is provided with a threaded hole  133  for a plug  134 . In the figure, the releasing/lifting cylinder is completely in the high position. The cylinder assembly has one or more venting conduits, which are not shown in the figure. In an operating situation in normal conditions, spaces S 2 - 56  and S are at the same pressure, the conduits C 1  and C 2  being connected to an external system so that the pressures and volume flow rates in different spaces correspond to the desired operating condition. Space S expands, and so does space S 3 , while space S 2  is reduced almost to its minimum size according to the distances of motion of the cylinder. 
   In  FIG. 6 , loading units are placed in a row on a supporting beam  12 . Most of them are part of a basic structure without a release and pull-back function. The piston  114  of the release and pull-back unit rests on the press shoe supporting beam  12  or alternatively hangs from the supporting beam. The projection  120  of the bracket  119  has been machined into a curved shape to fit the groove  118 . The curvature  150  changes at its ends to a more extended radius  151  that permits thermal motion of the piston  114  in relation to the supporting beam  12 . The bracket  119  has a space  152  for the flange  19  of the piston  114 . The space  152  is curved at its ends in the same way with a larger radius  153  than the radius  151  of the projection. The supply channel  36  leading into the oil supply space S 6  is placed eccentrically relative to the supply space S 6 . With this solution, free movement of the piston  114  on the supporting beam  12  due to thermal motion and adjustment is achieved, and at the same time the piston  114  allows the loading shoe to be lifted. 
     FIG. 7  illustrates the situation on the surface  16  of the loading shoe, without showing the press shoe  70  itself. Placed under the loading shoe is a row of loading units, most of which is part of the basic structure without release and pull-back action. The pull-back cylinder  71  is secured to the loading shoe by means of brackets  80 . The bracket  80  is so shaped that it has a curvature  155  on the side facing towards the cylinder  71 . Towards the extremities the radius  156  of the curvature  155  changes so as to allow thermal expansion of the cylinder  71  in the extreme position. According to adjustment, the cylinder  71  can move in the machine direction MD in relation to the brackets  80 . Between the brackets  74  and  80  in the CD direction of the machine, a small clearance  157  allowing thermal motion of the cylinder  71  is provided. The cylinder  71  has a release conduit C 2  and a fastening bore  158  corresponding to the conduit. In a release situation, a pressure p 2  is supplied via conduit C 2  into the cylinder inside cylinder  71 . Both the normal loading cylinder and the release cylinder  6 ,  71  are provided with a guide projection  28 , whose outer surface is  161 . Surface  161  may be cylindrical or curved or it may also have other suitable shapes. Between each cylinder  6 ,  71  there remains an unbroken neck  159  of the loading shoe. In the area of the projection  28 , a corresponding area has been machined away from the loading shoe. In normal operating conditions, the projection  28  is supported by its surface  160  on the loading shoe. During normal operation, the cylinders  6 ,  71  are immovable in relation to the loading shoe and follow the spatial position of the loading shoe. 
     FIG. 8  presents a cross-section of structure in which the loading shoe has an annular groove  165  machined at its upper end and correspondingly the shoe beam has a cylindrical space  166  machined inside it. Machined on the bottom of the cylindrical machined space  166  is a threaded hole  167 . Fitted in the machined space  166  is a separate circular adjusting plate  168 . The adjusting plate is provided with counterborings  169  and clearance holes  170  for fastening screws  171 . On the surface  172  of the adjusting plate is a machined projection  172  which fills space  165 . The adjusting plate  168  is fastened to bottom of the machined space  166  by means of fastening screws  171 . 
   This construction is typically only applicable for use in a nip structure below the nip point, where the shoe roll is below and the backing roll above, preferably on a vertical line. In this structural solution, in addition to moving in the lateral direction MD, the loading cylinder also moves the transverse direction CD of the machine. The structure is economical to manufacture, but the adjustment situation requires removal of the shoe beam from the machine and a “belt change situation”. 
   In the cross-section C-C in  FIG. 9   a ), that the groove  165  is concentric with the center of the loading cylinder. 
   In  FIG. 9   b ) it can be seen that the adjusting plate  168  its machined shoulder  173  are mutually eccentric by the amount of L 1 . In an initial situation, the machined shoulder  173  and the machined groove  165  in the loading cylinder are in one main direction on the same line with the machined space  166  in the shoe beam, see  FIG. 8 . In this situation, the whole row of loading cylinders are removed by the distance of L 1  in the CD direction of the machine. When the adjusting plate  168  is released and turned by the amount of the division angle γ between the fastening screws, the center of the loading cylinder moves correspondingly laterally in the direction of the angle γ and by the amount of the difference L 1 *1−cos γ in the direction of the center of machined space  166 , see  FIG. 8 . 
   The machined shoulder  173  turns about the center of the adjusting plate  166  with the diameter D=2*L 1 . The angle adjustment has maximum values when γ=90° or 270°. 
   The row of loading cylinders thus moves in relation to the basic adjustment position by max ±L 1  in the longitudinal direction MD of the machine and simultaneously by the amount of L 1  in the trans-verse direction CD of the machine. 
   In this structural solution, the shoe beam remains immovable in the transverse direction and in the longitudinal direction of the machine while position of the cylinders under the shoe beam changes. During operation, the cylinder can rotate about its axis. 
     FIG. 10 , which is a cross-section D-D of  FIG. 11 , presents a detail of a more sophisticated solution for movably connecting the cylinder  114  and the supporting beam  12  together. With this structure, a more extensive adjustment range is achieved than with the structure presented in  FIG. 6 . In its basic structure, bracket  175  is identical to bracket  119 , see  FIG. 6 . The cylinder  114  has additional projecting cams  176 , which go under the bracket  175  and, in a lifting situation, are pressed against the bracket  175 . The bracket  175  has a space  177  for the cam  176 , and likewise a space  178  for thermal expansion between the bracket  175  and the projecting cam  176 . The side of the bracket  175  facing towards the cylinder  114  has a curved shape, and it has been machined with radius larger than the flange  19 , taking thermal expansion tolerances into account. Like bracket  119 , bracket  175  is fastened to the supporting beam  12  with screws as described in  FIG. 4 . 
     FIG. 11  presents a second embodiment of the release cylinder of a shoe press that simultaneously functions as a loading cylinder as well. Added to the cylinder part  71  are projecting cams  189 , and likewise to the piston part  114 . The projecting cams  189  go into a space  181  in the bracket  180  below the press shoe  70 . On the side facing towards the oil supply channel, the projecting cam  189  is beveled to an oblique shape according to surface  182 . Correspondingly, the cover part of the oil supply channel is beveled in the area of the projecting cam to an oblique shape according to surface  183 . Thus, between surfaces  182 , 183  there is formed a space  191  that allows the cylinder  71  to move in a lateral direction MD. On the upper surface  188  of the cylinder  71  are two machined oval grooves L 2 ,L 3  at different distances in the CD direction of the machine. Thus, by turning the cylinder through 180° about its center, the center of the cylinder is caused to move through a distance corresponding to the difference between amounts L 2  and L 3  in a desired direction in the MD direction of the machine, in other words, a second basic adjustment is achieved. 
   In space  184  is set a toothed wheel pin  187 , which is eccentric relative to the center of the toothed wheel  186 . Placed contiguously with the toothed wheel  186  is a toothed rack  185 . By turning the toothed wheel through 180°, the cylinder  71  can be moved further via automatic adjustment by 2*the eccentricity of the toothed wheel in the MD direction of the machine. According to an embodiment, the total movement can be selected between ±0-20 mm. 
     FIG. 12  presents a more detailed cross-section E-E of  FIG. 11 . It can be seen from the structure that the basic solution is similar to the fastening of the piston  114  to the supporting beam  12 , see  FIG. 10 . Between the projecting cam  189  of the cylinder  71  and the bracket  180 , a space  195  is provided to allow for thermal expansion. On the lower surface  190  of the shoe beam, see  FIG. 11 , a machined space  197  is provided for the toothed rack  185  and the toothed wheel  187 . The toothed rack  185  moves in the groove  197  in the CD direction of the machine and is supported by its lateral surfaces on space  197  and on the upper surface  188  of the cylinder  71 , and similarly the toothed wheel  186  rotates in space  196  according to the movement of the toothed rack  185  and is supported by its lateral surfaces on space  196  and on the upper surface  188  of the cylinder  71 . Machined guides  198  have been machined away from the upper surface  188  of the cylinder  71 , and the cylinder  71  is guided by the lateral surface  201  of the machined guide  198  according to surface  200 . 
   The cylinder  71  has two identical guide surfaces  201 , so the guiding motion in the MD direction takes place between the two guide surfaces in the direction determined by the toothed rack  185  and the toothed wheel  186 . The wedge machining  199  may be machined directly in the shoe beam or it may be made using a separate wedge solution. It is also possible to shape the upper end of the cylinder in such a way that the cylinder itself will act as a wedge element, in which case the shoe beam has a wide wedge machining machined on its bottom. 
   Part of the toothing  202  of the toothed rack has been removed from between the cylinders, not shown in the figure. This ensures that the distribution of the cylinders will not change in the CD direction of the machine and the tooth pitch will not change the mutual distance of the cylinders. 
   The toothed rack  185  is moved in the CD direction of the machine automatically by means of a cylinder  203 . The cylinder  203  consists of an actual cylinder tube  204  and a piston  205 . The press shoe  70  is provided with threaded holes  206  for the fastening bolts  207  of the cylinder. The mounting flange  210  is provided with clearance holes  208  and counterborings  209  for the fastening bolts  207 . The cylinder  204  comprises the mounting flange  210 , too, either as a welded structure or an assembly made in some other way. 
   The end of the toothed rack  185  is provided with a threaded hole  211  and correspondingly the second end of the piston  205  is provided with a fastening thread  212 , by means of which the piston  205  is locked to the toothed rack  185 . The piston  205  consists of a piston part  213  and a rod  214 . At the second end of the rod is the aforesaid fastening thread  212 . The rod has additionally a width across flats, not shown in the figure. The piston part  213  is provided with a sealing groove  215  and a seal  216 . 
   Inside the cylinder  204  is a cover part  217  with a threaded outer surface and inside the cover on the side of the piston rod  214  a sealing groove  218  and a seal  219 . 
   The conduit for the supply of pressurized oil to the back side of the piston  213  is referred to by number  220  and the conduit to the front side by  221 . Inside the cylinder are additionally the required channel bores and pluggings of additional bores, as well as venting conduits, not shown in the figure. At the other end of the shoe beam is a corresponding transfer system, as can be seen from the figure. 
   The operating principle is that the cylinder at one end pushes the toothed rack while the cylinder at the other end correspondingly pulls the toothed rack in the direction desired in each situation. As a result of the movement, the toothed wheel rotates in its housing and moves the cylinder in one direction or the other in the MD direction of the machine in relation to the shoe beam. The shoe beam always remains immovable but the cylinder moves. This motion takes place in an unloaded state and the cylinder is, however, lifted by a separate pressure system so that it rests on an oil film. The system also permits other operating variants and is not exclusively limited to the described mode of operation. 
   According to  FIG. 13   a  and  13   b , the lower surface of the press shoe  70  is provided with wedge machinings  199  between each cylinder. The side surface  200  of the wedge machining  199  goes against the surface  201  of the cylinder  71 .  FIG. 13  a shows the toothed wheel  186  as a detached part, as well as the space  196  in the lower surface  190  of the press shoe  70  where the toothed wheel  186  rotates. The wedge machinings  199  can also be implemented as an actual wedge/screw joint. In this case, the bottom of the shoe beam is first machined to make it straight and only then are the actual wedge slots and the threads for the fastening screws machined. 
     FIG. 13   b  shows the situation above the supporting beam  12  as seen from the side of the shoe. The cylinders are placed between the wedge machinings and follow the thermal motion of the shoe beam in the CD direction of the machines. As they are moving, the cylinders move the pistons on the supporting beam with them. The shoe beam is secured by a point on the center line of the machine or by a point in the immediate vicinity of said line. Functionally, the shoe beam can thus expand and move in both directions relative to the center of the machine. In respect of their construction, the normal loading cylinder and the cylinder designed for releasing/lifting only differ from each other in respect of the inner piston and the manner in which they are secured externally. 
     FIG. 14  illustrates an alternative structural solution for bi-directional adjustment of “tilt”, wherein the shape of the projection  28  is machined in the way shown in the figure. Surfaces  229 , 230  are mirror images of each other. In an initial situation, the pull bars/push bars  225 , 226  are in a position as shown in  FIG. 14   a , and with a maximum adjustment they are in a position as shown in  FIG. 14   b . In the initial situation, the cylinder  71  is eccentric relative to the center line CL of the bars  225 , 226  by the amount of y, and in the final situation on the other side of the center line CL by the amount of y 1 . In this case, the cylinder  71  thus moves from a higher position towards a lower position in the MD direction of the machine. 
   The machined guide surfaces  227 , 228  on the bars  225 , 226  are as shown in the figure. When the bars  225 , 226  are being moved in the CD direction of the machine, one to the right and the other correspondingly to the left of the vice versa, one of the machined guide surfaces  227 , 228  forces the cylinder  71  to move in the desired direction while the other machined guide surface correspondingly makes room on the side of the movement. The action is completely automatic and takes place from the outside of the roll according to control, without a need to dismantle the device. The distance moved through is measured by a linear sensor, not shown in the figure. When the machine is working in normal operation, the linear sensor continuously supplies information about the state of the adjustment and the need to alter the adjustment if for some reason the set adjustment undergoes any change in the MD direction of the machine during operation. For different product qualities, it is possible to find the best position for the shoe beam according to dry matter and other operating parameters and to adjust the beam accordingly before quality change. 
   In respect of their structure and adjustment properties, the normal cylinder and the releasing/lifting cylinder do not differ from each other. About every 5th cylinder is a lifting/releasing cylinder, unless otherwise required by special reasons. 
     FIGS. 15   a  and  15   b  further present an alternative structural solution for machining the projection  28  and shows the corresponding side dimensions k and k 1 , corresponding to values y and y 1 , see  FIG. 14 , in bi-directional automatic “tilt adjustment”. In other respects the structure corresponds to that described in  FIG. 14 . 
     FIG. 16  presents a basic solution for manual bi-directional “tilt adjustment”. In this case adjustment is only possible when the machine is in standstill state and the surface fabric of the roll removed from the machine. The stop faces of surfaces  161  of the projection  28  are concave surfaces consisting of a straight portion and curved portion, surfaces  235 , 236  are mirror images of each other and are placed in somewhat overlapping positions in the CD direction of the machine, as was also described earlier in connection with  FIGS. 14 and 15 . Curved surfaces  235 , 236  are the basic solution in the development trajectory while FIGS.  14 , 15  represent more refined versions of the theme. The later versions have the advantage of a notably large contact surface between the projection  28  and the guide bars  225 , 226 , the surface pressure between the surfaces being thus within allowed limits. The end  222  of the press shoe  70  is provided with threaded holes  237  for the fastening bolts  239  of an adjusting frame  238 . Inside the adjusting frame  238  is a space  240  for the actual adjustment length. The fastening end  241  of the adjusting bars  225 ,  226  moves in space  240 . Inside the fastening end  241  is a threaded hole  242  for the threaded end  244  of an adjusting bolt  243 . The other end of the adjusting bolt  243  is correspondingly provided with a thread  245  for adjustment. Actual adjustment is performed by turning the lock nut  246  in the desired direction (loosening or tightening) and correspondingly from the other end of the shoe beam the bar is tightened or loosened by the desired distance by turning the other identical adjusting nut, thus moving the adjusting bar in the CD direction of the machine. In overall adjustment, one of the adjusting bars has to be loosened first and only then is the other one tightened in the opposite direction, thereby moving the row of cylinders in the direction of the loosened bar. 
   In manual adjustment no separate linear sensor is needed for measuring the distance of sideways movement, unless it is desirable to know this value e.g. for reasons of control to determine how much the center of the cylinder deviates from the nominal center line of the shoe beam. The adjustment can be measured with sufficient accuracy from the length of the portion of the adjusting bolt  243  protruding from the outer surface of the adjusting frame  238 . Inside the adjusting frame are counterborings  247  and clearance holes  248  for the fastening bolts  239 . 
     FIG. 17  presents a basic solution for automatic bi-directional “tilt adjustment”. The structure is in principle identical to the cylinder in  FIG. 12 . The difference to the structure described above is a second through-going piston rod  250  at the second end of the cylinder. In addition, the back end of the cylinder is provided with a sealing groove  251  and a seal  252 . The cylinder is fastened to the adjusting bars  225 , 226  in the same way as in  FIG. 16 . Identical cylinders acting on the same guide bar are provided at both ends of the shoe beam. 
   The operation is such that simultaneously one cylinder pair consisting of the pulling and pushing cylinders acting on the same bar moves e.g. bar  225  to the right and correspondingly the other cylinder pair moves bar  226  to the left. The action takes place under hydraulic control. An operating diagram will be presented later on. When the linear sensor, not shown in the figure, measures the desired sideways movement in the MD direction of the machine, the system is locked into a locked state and the flow between different cylinders stops. The adjusting bars  225 , 226  now remain in their current position, the relevant position data is passed to the machine&#39;s logic system or equivalent. 
     FIG. 18  presents a cross-section F-F of  FIG. 16 , i.e. an end view as seen from the end of the shoe beam. The basic idea in the structure is identical to that in  FIG. 20  without automatic adjustment. Generally speaking, a manually adjusted construction is suited for use in applications of simpler technology and can be modified structurally to make it automatically adjustable if necessary. 
     FIG. 19  is a cross-section G-G of  FIG. 18 . It shows a situation as seen from the end of the shoe beam. The construction is in principle identical to that of the manual adjusting device in  FIG. 18 , and manual adjustment can be replaced with an automatic unit if necessary. 
     FIG. 20  presents a cross-section H-H of  FIG. 12 , i.e. an end view of the automatic toothed rack/toothed wheel “tilt adjustment”. The mounting flange  210  of the cylinder  203  is secured to the end surface  222  of the press shoe  70 . The oil supply conduits are directed in the direction considered best. 
     FIG. 21  presents a diagram illustrating the principle of the hydraulic system in unidirectional automatic “tilt adjustment”. Direction  1  corresponds to pressure P 1 , in this case the movement of the system is to the right in the figure. The cylinders  203 , 264  are of identical construction and their internal structure is described in  FIG. 12 . The pressure converters  262 , 263  are in main principle identical to the cylinders  203 , 264 , the internal structure is not show. The pressure P 1  is conveyed into chambers  260 , 261 , the pressure in chamber  261  increases the pressure in chamber  265  and the pressure increases in chamber  267 , corresponding to the pressure in chamber  260  in the proportion of the areas. The pull bar  271  is under the same force as bar  272 . From the chambers  266 , 270  the overpressure is discharged into a container via conduit F 1 . From space  268  the pressure is discharged into space  269 . During movement  1 , conduits P 2 /T 1 , F 2  and the quick couplings are closed. 
   Correspondingly, during movement  2 , in the figure from right to left, the pressure is passed from conduit P 2  into chambers  269 , 268  and the pressure from space  267 , 265  is discharged into the tank via conduit F 2 . From space  270  the pressure is conveyed into space  266 . Conduits P 1 /T 2 ,F 1  and the quick couplings are closed. From chamber  260 , the pressure is conveyed into space  261 . During movement  2 , bar  272  is the pulling bar and correspondingly bar  271  is the pushing bar. Position  273  is an oil pump and positions  274 , 275 , 276 , 277  are shut-off valves. The system allows overall control of forces and pressures at both ends of the toothed rack  185  during movements in different directions. 
   The diagram only presents a solution with a manual pump, but the external actuator can be completely replaced with an automatic solution and dual-function shut-off valves. Each situation will then be taken care of under control of the automatic system. When the machine is running, the system is shut off in a locked state. 
   The magnitude of tilt adjustment is obtained as a magnitude of the linear sensor from the automation system. 
     FIG. 22  presents a diagram showing the main features of bi-directional automatic “tilt adjustment”. Cylinders  280 , 281 , 282 , 283  are of a construction identical to that described in  FIG. 17 . Diagram  284  represents a manually operated pressure unit for the assembly in question, but the pressure unit  284  can also be implemented as a completely automatic unit. If the bars  225 , 226  are to be moved in the direction of arrow  1 , then the pressure is conveyed from the pressure unit  284  into chambers P of cylinders  280 , 281 . As the pressure is increasing on the P side, the pressure on the T side increases correspondingly and thus the pressure is transmitted from the T side of cylinders  280 , 281  to the P side of cylinders  282 , 283 . Correspondingly, the pressure increases on the T side of cylinders  282 , 283  and the pressure is discharged via the pressure unit  284  into the container. Since the pistons have equal surface areas, the pressures on different sides of the pistons are correspondingly also equal. Lines  285 , 286  are needed for internal filling and venting of the structure. If the bars  225 , 226  are to moved in the direction of arrow  2 , then the pressure and tank lines are interchanged in lines  287 , 288 , as a result of which the direction of motion of the bars  225 , 226  changes. The change of direction is effected by means of valve  289 . The required magnitude of tilt adjustment is obtained from the automation system as a setting of the linear sensor. When the machine is in operation, the system is shut off into a locked state and checked if necessary by means of either manually or automatically actuated valves  290 , 291 , 292 , 293 . The pressure unit  284  can be either detached from the machine or kept continuously in an operating condition. 
   By the solution presented in the diagram, the lateral guide bars of the loading cylinders can be caused to move in a desired direction and thus the position of the loading cylinders can be changed in the longitudinal direction MD of the machine in the manner described above. 
   Typically, the press shoe is supported during the movement by preventing its movement in the machine direction by using a supporting element (not shown in the figures). Supporting elements are typically arranged on opposite sides of the press shoe in the machine direction. 
   If desirable, the second cylinder-piston unit of the loading unit can also be used to enhance the loading of the shoe press. 
   It is conceivable that the device of the invention is used in the converse manner so that the adjustment is on the side of the supporting beam and the means for reducing lateral forces are on the side of the press shoe. 
   It is obvious to the person skilled in the art that the invention is not limited to the embodiments described above, but that it may be varied within the scope of the claims presented below. Depending on the embodiment, features that may have been presented together with other features in the description part can also be used separately from each other.