EP2808445B1 - Deflection compensated roll - Google Patents
Deflection compensated roll Download PDFInfo
- Publication number
- EP2808445B1 EP2808445B1 EP13169860.7A EP13169860A EP2808445B1 EP 2808445 B1 EP2808445 B1 EP 2808445B1 EP 13169860 A EP13169860 A EP 13169860A EP 2808445 B1 EP2808445 B1 EP 2808445B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- roll
- loading
- damping
- tolerance
- loading element
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000013016 damping Methods 0.000 claims description 50
- 239000000835 fiber Substances 0.000 claims description 14
- 239000007788 liquid Substances 0.000 description 30
- 239000003921 oil Substances 0.000 description 17
- 230000001419 dependent effect Effects 0.000 description 7
- 230000007423 decrease Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000001050 lubricating effect Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000003044 adaptive effect Effects 0.000 description 2
- 239000011888 foil Substances 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000009182 swimming Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001035 drying Methods 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000004806 packaging method and process Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Images
Classifications
-
- D—TEXTILES; PAPER
- D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
- D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
- D21G1/00—Calenders; Smoothing apparatus
- D21G1/02—Rolls; Their bearings
- D21G1/0206—Controlled deflection rolls
- D21G1/0213—Controlled deflection rolls with deflection compensation means acting between the roller shell and its supporting member
-
- D—TEXTILES; PAPER
- D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
- D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
- D21G1/00—Calenders; Smoothing apparatus
- D21G1/0073—Accessories for calenders
- D21G1/008—Vibration-preventing or -eliminating devices
-
- D—TEXTILES; PAPER
- D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
- D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
- D21G1/00—Calenders; Smoothing apparatus
- D21G1/02—Rolls; Their bearings
- D21G1/0226—Bearings
Definitions
- the invention relates to a deflection compensated roll according to the preamble of claim 1.
- the deflection compensated roll is a nip roll for a calender of the fiber web machine.
- a typical production and treatment line comprises a head box, a wire section and a press section as well as a subsequent drying section and a reel-up.
- the production and treatment line can further comprise other devices and sections for finishing the fiber web, for example, a sizer, a calender, a coating section.
- the production and treatment line also comprises at least one winder for forming customer rolls as well as a roll packaging apparatus.
- fiber webs are meant for example a paper, board, tissue webs. In each section and device vibrations may occur in several different components.
- vibrations may occur in a nip, which is formed in between two elements, typically between two rolls but also the nip can be formed with a roll, a belt, a shoe or corresponding element and a counter-element of corresponding or different kind, often at least one of the nip forming elements is a roll.
- the roll can be a deflection compensated roll, which are used in nips of the press section and of the calenders of the fiber web machine.
- water is removed from the fiber web and in the calender nips the fiber web is treated for example to achieve certain surface properties such as gloss.
- the fiber web is passed through the nip freely or supported by a belt, a felt, a wire or a corresponding fabric.
- the fiber web is pressed in order to remove water from the web or to effect to the properties of the web and by the deflection compensated roll the nip pressure is controlled in cross-direction or the fiber web i.e. in the longitudinal direction of the roll.
- one vibration form is barring which is caused by resonance of a roll pair, in which the calender vibrates such that nip load varies.
- the variations in nip load gradually form the soft cover of the calender such that the cross section of the roll will be angular.
- the resonance of roll pairs of calenders is unavoidable and only size of rolls and frames have influence on the frequencies on which the resonance occurs.
- the amplitude of vibration is limited only by damping in the mechanical system i.e. the heat energy created by the vibration of elements of the system. Damping is observed for example as internal hysteresis of materials (very little effect), in connections with friction, as friction losses on glide-surfaces.
- the largest damping occurs in connection with movements of pistons of loading elements of the deflection compensated roll. It should be noted that the movement must be long enough in order not to remain only as elastic deformation of seals of the loading elements.
- a deflection compensated roll comprises a shell around the loading shaft with loading zones in which loading shoes with a piston are arranged.
- the loading zones are connected to the shell of the roll rigidly, since thicknesses of lubricating oil between the loading shoes and the shell are thin.
- the loading shoes are supported on the loading shaft by means of a pressure medium volume, typically an oil volume and also this medium volume is significantly rigid, since as the piston moves the moving medium area is large and flow channels are very narrow.
- DE-A-102005049524 is disclosed a a deflection-compensated roll in a paper machine which the roll has a shell and is supported on it by supporting elements pressed against the inside of the sleeve with the aid of a hydraulic pressure medium, where each element comprises a radially-moveable shoe pressing against the inside of the roll and a radially-moveable piston. Also the roll includes elements between the shoe and the piston by means of which vibration transmitted from the nip is transferred from the shoe to the piston.
- EP 1411254 B1 is disclosed a middle roll of a calender with a damper assembly having an inertial mass.
- the roll has a roll shell that surrounds an internal space, in which there is arranged a damper assembly having at least one passive oscillation damper that has a damper frequency which lies below a natural frequency of the roll, or a roll system containing the rolls, that is critical for the formation of barring.
- a damper assembly having at least one passive oscillation damper that has a damper frequency which lies below a natural frequency of the roll, or a roll system containing the rolls, that is critical for the formation of barring.
- the middle roll at least in a region between the oscillation damper and the roll shell, the internal space is filled with liquid, the viscosity of which exceeds a predetermined minimum amount.
- the damper will be set to a certain frequency for damping.
- the roll disclosed is a tube roll not a deflection compensated roll.
- An object of the invention is to create a deflection compensated roll and in which the disadvantages and problems of prior art are eliminated or at least minimized.
- an object of the invention is to provide a deflection compensated roll for a calender of a fiber web machine.
- the deflection compensated roll according to the invention is characterized by the features of the characterizing clause of claim 1.
- a new way of controlling vibrations in a deflection compensated for example a zone controlled roll for a calender is created, in which the vibrations are controlled with the help of loading means of the deflection compensated roll and/ or with the help of support means of the deflection compensated roll.
- the support means may be the bearing support to the frame of the calender for the shaft ends of the roll or the loading cylinder support of the calender.
- optimum design of at least one roll is provided by vibration modeling simultaneously combining limitations of static loading and providing optimal amplitude of movement in the loading elements of the at least one roll in the / in those natural frequency / frequencies that cause nip pressure or nip load variation in the nip formed by the deflection compensated roll with another roll.
- the deflection compensated roll is designed and damping means are designed for the at least one loading element and advantageously for the support of the roll. It should be noted that prior art design methods of calender rolls do not take into account any parameters relating to vibration or its damping and when vibration occurs in use of the calender rolls solutions are sought to dampen the vibration i.e. action is taken only after the problems occur.
- the hydraulic piston of a loading element of the deflection compensated roll is separated from the loading element by resilient connection, i.e.
- the loading element is located in the pressure pocket of the shaft such that there is a significant tolerance between the loading element and the pressure pocket.
- the tolerance is 0,5 -2,5 mm, advantageously 1,0 - 2,0 mm.
- this tolerance is advantageously not sealed and the loading element floats in the medium, advantageously in oil.
- the loading element When the loading element is under vibration it moves the medium in the volume between the piston and the loading element, which medium is pressurized and forced to flow in the tolerance of the pressure pocket of the loading element. In the tolerance the medium flow creates pressure loss that is in direct relationship with movement velocity of the loading element and thus functions as a viscous damper.
- the deflection compensated roll comprises a resilient element, which is a disc spring which is located between the piston of the at least one loading element of the roll and support of the at least one loading element is provided freely movable in the loading direction of the at least one loading element.
- the hydraulic piston of the loading element may also be loaded by a high pressure gas volume, which will be significantly more compressible than oil.
- a separate oil feed line is arranged for the lubrication of the loading element.
- Leakage free air loaded zones of the roll also make it possible to use simple and compact solenoid valves for pressure control of the loading zones.
- Complicated servo/proportional valves are not needed, but instead pressure is controlled by adjusting the opening and closing times of the solenoid valves. Such control is known as digital pressure control.
- the shell of the deflection compensated roll vibrates, at least one loading element moves with the shell as only thin foil of medium is between the shell and the loading element.
- the loading element moves towards the shaft of the roll, it causes a medium flow into the tolerance with high flow speed due to the narrowness of the tolerance and a flow loss is caused.
- the flow loss is dependent on viscosity of the medium, dimensions of the tolerance and thus at a certain movement speed a pressure loss is created which is dependent on the cross-sectional flow area of the tolerance and by this the damping force is created.
- the optimum damping design can be calculated such that the vibration damping by loading elements will provide its maximum under different vibrations.
- the vibration damping can further be influenced during operating the calender, as damping is dependent from the viscosity of the medium and adjustment of viscosity of the medium is provided by adjusting the temperature of the medium and thus also adaptive vibration damping can be achieved.
- the stiffness of the loading elements is in the range of 1 x 10 5 N/m - 1 x 10 7 N/m and damping is the range of 1 x 10 5 Ns/m - 1 x 10 6 Ns/m.
- the roll support stiffness is advantageously 1 x 10 7 N/m -5 x 10 8 N/m.
- the roll support damping is advantageously 5 x 10 5 Ns/m -5 x 10 7 Ns/m.
- the desired damping properties are designed to the roll.
- the deflection compensated roll is designed for a roll nip of a calender such that total damping is maximized by taking into account all resonances in the roll causing pressure variations in the nip area.
- the deflection compensated roll is supported by its shaft ends to the frame of the by resilient support and by a bearing.
- a vibration damping support of the roll is provided by liquid film damping, i.e. squeeze film damping.
- the shaft of the roll moves oil in a tolerance of a bearing housing
- the oil film in the tolerance is squeezed between hard surfaces and forced to flow in the narrow gap volume. Pressure loss in the flow creates an opposite force and damping is achieved. Damping force is dependent on viscosity of the liquid, height of the tolerance and width of the shaft and the liquid film sector dimensions.
- support of the deflection compensated roll is provided by construction the bearings of the roll on support of a separate bushing which is supported in the loading direction to the respective bearing house by pressure pockets.
- the pressure pockets are filled for supporting the load pressurized gas, for example air, which has high compressibility.
- the area and volume of the pressure pocket is designed to provide desired compliance of the support.
- liquid pockets that are filled with oil or other liquid. The tolerance between the liquid pockets and the bushing and the sector covered by the liquid pockets and the area of the liquid pockets give the different factors to design the liquid volume such that desired viscous damping is provided.
- the support arrangement can also be fitted in the fixing points of calender loading cylinders.
- the damping is provided such that when the bushing moves in loading direction at the other end of the liquid volume the tolerance decreases and at the other end the tolerance increases. As the liquid flows in the narrow tolerance according to the replacement volume pressure loss is created in the flow and thus an opposing force to the movement is provided.
- the stiffness and damping properties of the support of the deflection compensated roll are designed.
- the deflection compensated roll is loaded in the calender by loading cylinders provided with resilient support.
- vibrations damping support is provided by liquid film damping, i.e. squeeze film damping, in which in loading direction the force is carried by a high pressurized gas pocket and the shaft of the loading cylinder is "floating" on a small tolerance defined by discharge amount and throttling of the inlet side.
- figure 1 is shown schematically an example of the invention.
- figure 2A is shown schematically an example of an advantageous loading element according to the invention.
- figure 2B is shown schematically another example of a loading element which example does not fall under the scope of the claims.
- figure 3 is shown schematically an example of an advantageous bearing arrangement according to an advantageous feature of invention.
- figure 4 is shown schematically in further detail the liquid flow in liquid pockets of the example of figure 3 .
- figure 5 is shown schematically another example of an advantageous bearing arrangement according to an advantageous feature of invention.
- FIGS 6 and 7 are schematically shown an example of schematic example a swimming roll.
- FIG. 8A - 8B is shown schematically an example the loading cylinder support of the calender.
- a nip N for example a calender nip, is formed between a deflection compensated roll 10 and its counter roll 11.
- the counter roll 11 is supported by its shaft ends 13 by a vibration damping element 15 and by a spring element 17 to the frame structure of the device, for example the calender.
- the deflection compensated roll 10 is supported by its shaft ends 12 by a vibration damping element 14 and by a spring element 16 to the frame structure of the device for example the calender.
- On the shaft 12A of the deflection compensated roll 10 are supported loading elements 20 of which only one is marked by reference numeral for clarity reasons.
- the loading elements 20 load the shell 10A of the roll in the nip direction, as shown in the figure, i.e. towards the counter roll 11 of the deflection compensated roll 10.
- Each loading element 20 is also provided with a damping element 24 and a spring element 26.
- the optimum damping design can be calculated such that in vibration modes the vibration damping by loading elements is maximized.
- the vibration damping can further be influenced during operating the calender, as damping is dependent from the viscosity of the medium and adjustment of viscosity of the medium is provided by adjusting the temperature of the medium and thus also adaptive vibration damping can be achieved.
- FIG 2A is the example of the loading element 20 loads the shell 10A and it is located in a pressure pocket of the shaft 12A of the deflection compensated roll10.
- the loading element 20 comprises a loading shoe 23, which has oil pockets 25 for lubricating medium, for example oil.
- the lubricating medium is passed to the oil pockets 25 via channels 27.
- the hydraulic piston 21 is separated from the loading element 20 by the resilient spring element 26, by a disc spring and seals 35 seal the loading pressure pocket 33 of the piston 21.
- the loading element 20 is located in the pressure pocket 33 of the shaft 12A such that there is a significant tolerance 31 between the loading element 20 and the pressure pocket.
- the tolerance is 0,5 - 2,5 mm, advantageously 1,0 - 2,0 mm.
- the loading element 20 floats in the medium, advantageously in oil.
- the cross section of the element deviates from circular form, for example it may have grooves for providing cross-sectional flow area (not shown).
- Below the spring element 26 is the piston 21 that provides the loading force for the loading element 20, as shown by arrows.
- the piston 21 is sealed in the pressure pocket 33 by seals 35.
- the hydraulic piston 21 of the loading element 20 may also be loaded by a high pressure gas volume in loading pocket 33 sealed by seals 35 as shown in figure 2B .
- the loading element 20 comprises a loading shoe 23, which has oil pockets 25 for lubricating medium, for example oil.
- a separate oil feed line 38 is arranged for the lubrication of the loading element 20.
- the piston 21 of the loading element 20 of is separated from the loading element 20 by the gas space 39 sealed by seals 35, 36.
- the loading element 20 is located in the pressure pocket 33 of the shaft 12A such that there is a significant tolerance 31 between the loading element 20 and the pressure pocket.
- the tolerance is 0,5 - 2,5 mm, advantageously 1,0 - 2,0 mm.
- a deflection compensated roll 10 comprises a shell 10A around the loading shaft 12A with loading zones provides by the loading elements 20 pistons 21.
- the loading zones are connected to the shell 10A of the roll 10 rigidly, since thicknesses of lubricating oil between the loading elements 20 and the shell 10A are thin.
- the loading elements 20 are supported on the loading shaft 12A by means of a pressure medium volume.
- the loading and vibration damping is provided such that when the shell 10A of the deflection compensated roll 10 vibrates the at least one loading element 20 moves with the shell 10A as only thin foil of medium is between the shell 10A and the loading shoe 23 of the loading element 20.
- FIG 3 is shown a schematic example of the shaft end 12 bearing house 41, in which around bearing 43 an oil film is provided in tolerance i.e. liquid pocket 45 between the bearing 43 and the bearing house 41.
- the loading direction is marked by arrow LD.
- Pressure pockets 47 are provided in the loading direction LD.
- Seals 49 are located between the pressure pockets 47 and liquid pockets 45.
- the support of the shaft ends 12 of the roll 10 has a separate bushing 50 which is supported in the loading direction LD to the respective bearing house 41 by pressure pockets 47.
- the pressure pockets 47 are filled with pressurized gas, for example air, which high compressibility.
- the area and volume of the pressure pocket 47 is designed to provide desired compliance of the support.
- Perpendicular to the loading direction LD is additionally provided liquid pockets 45 that are filled with oil or other liquid. The tolerance between the liquid pockets 45 and the bushing 50 and sector covered by the liquid pockets 45 and area of the liquid pockets 45 give the different factors to design the liquid volume such that desired viscous damping is provided.
- the damping is provided such that when the bushing 50 moves in loading direction LD at the other end of the liquid volume the tolerance decreases and at the other end the tolerance increases. As the liquid flows in the narrow tolerance according to the replacement volume pressure loss is created in the flow and thus an opposing force to the movement is provided.
- a swimming roll 60 is provided by a spring (not shown) in the loading element 62, which loading element is similar to figure 2 .
- the spring follows the shell 65 and thus compensates the movement and vibration damping is provided.
- FIGS 8A - 8B is shown schematically an example the loading cylinder support 70 of the calender, with resilient support.
- vibrations damping support is provided by liquid film damping, i.e. squeeze film damping, in which in loading direction the force is carried by a high pressurized gas pocket 71, which corresponds to pressure pocket 47 of figures 3 and 5 and the shaft of the loading cylinder is "floating" on a small tolerance defined by discharge amount and throttling of the inlet side.
- a cone structure 72 provides the positioning of the shaft of the loading cylinder and functional tolerances are provided by axial tightening means 73.
- Hydraulic pockets 74 In direction perpendicular to the loading the shaft positions by hydraulic pockets 74, in which oil is fed into middle of the pockets and discharged from edge grooves of the pockets and operation of which corresponds to that of liquid pockets 45 of figures 3 - 5 . Hydraulic pockets 74 also provide viscous dampening by squeeze film effect.
Landscapes
- Paper (AREA)
- Rolls And Other Rotary Bodies (AREA)
Description
- The invention relates to a deflection compensated roll according to the preamble of claim 1. Especially the deflection compensated roll is a nip roll for a calender of the fiber web machine.
- In fiber web machines the fiber web is produced and treated in an assembly formed by a number of apparatuses arranged consecutively in a process line. A typical production and treatment line comprises a head box, a wire section and a press section as well as a subsequent drying section and a reel-up. The production and treatment line can further comprise other devices and sections for finishing the fiber web, for example, a sizer, a calender, a coating section. The production and treatment line also comprises at least one winder for forming customer rolls as well as a roll packaging apparatus. In this description and the following claims by fiber webs are meant for example a paper, board, tissue webs. In each section and device vibrations may occur in several different components. For example vibrations may occur in a nip, which is formed in between two elements, typically between two rolls but also the nip can be formed with a roll, a belt, a shoe or corresponding element and a counter-element of corresponding or different kind, often at least one of the nip forming elements is a roll. The roll can be a deflection compensated roll, which are used in nips of the press section and of the calenders of the fiber web machine. In the press nips water is removed from the fiber web and in the calender nips the fiber web is treated for example to achieve certain surface properties such as gloss. The fiber web is passed through the nip freely or supported by a belt, a felt, a wire or a corresponding fabric. In the nip the fiber web is pressed in order to remove water from the web or to effect to the properties of the web and by the deflection compensated roll the nip pressure is controlled in cross-direction or the fiber web i.e. in the longitudinal direction of the roll.
- In calender design of prior art the only dynamical aspects taken into account are unbalance and off-roundness of rolls and first critical speed of rolls. The design of rolls, frames and loading means is done by examining minimum and maximum values of static loading and by ensuring that the criteria of tension or deflection is not exceeded and the first natural frequency of the structure is above maximum roll rotation frequency.
- In calenders one vibration form is barring which is caused by resonance of a roll pair, in which the calender vibrates such that nip load varies. The variations in nip load gradually form the soft cover of the calender such that the cross section of the roll will be angular. The resonance of roll pairs of calenders is unavoidable and only size of rolls and frames have influence on the frequencies on which the resonance occurs. In resonance situations the amplitude of vibration is limited only by damping in the mechanical system i.e. the heat energy created by the vibration of elements of the system. Damping is observed for example as internal hysteresis of materials (very little effect), in connections with friction, as friction losses on glide-surfaces. In calender the largest damping occurs in connection with movements of pistons of loading elements of the deflection compensated roll. It should be noted that the movement must be long enough in order not to remain only as elastic deformation of seals of the loading elements.
- A deflection compensated roll comprises a shell around the loading shaft with loading zones in which loading shoes with a piston are arranged. The loading zones are connected to the shell of the roll rigidly, since thicknesses of lubricating oil between the loading shoes and the shell are thin. The loading shoes are supported on the loading shaft by means of a pressure medium volume, typically an oil volume and also this medium volume is significantly rigid, since as the piston moves the moving medium area is large and flow channels are very narrow.
- In
DE-A-102005049524 is disclosed a a deflection-compensated roll in a paper machine which the roll has a shell and is supported on it by supporting elements pressed against the inside of the sleeve with the aid of a hydraulic pressure medium, where each element comprises a radially-moveable shoe pressing against the inside of the roll and a radially-moveable piston. Also the roll includes elements between the shoe and the piston by means of which vibration transmitted from the nip is transferred from the shoe to the piston. InEP 1411254 B1 is disclosed a middle roll of a calender with a damper assembly having an inertial mass. The roll has a roll shell that surrounds an internal space, in which there is arranged a damper assembly having at least one passive oscillation damper that has a damper frequency which lies below a natural frequency of the roll, or a roll system containing the rolls, that is critical for the formation of barring. According to one example of the middle roll at least in a region between the oscillation damper and the roll shell, the internal space is filled with liquid, the viscosity of which exceeds a predetermined minimum amount. In this roll the damper will be set to a certain frequency for damping. The roll disclosed is a tube roll not a deflection compensated roll. - An object of the invention is to create a deflection compensated roll and in which the disadvantages and problems of prior art are eliminated or at least minimized.
- In particular an object of the invention is to provide a deflection compensated roll for a calender of a fiber web machine.
- In order to achieve the above mentioned objects the deflection compensated roll according to the invention is characterized by the features of the characterizing clause of claim 1.
- By the invention a new way of controlling vibrations in a deflection compensated, for example a zone controlled roll for a calender is created, in which the vibrations are controlled with the help of loading means of the deflection compensated roll and/ or with the help of support means of the deflection compensated roll. The support means may be the bearing support to the frame of the calender for the shaft ends of the roll or the loading cylinder support of the calender.
- In the method for controlling vibrations of the fiber web machine, in particular of a deflection compensated, for example of a zone controlled roll, optimum design of at least one roll is provided by vibration modeling simultaneously combining limitations of static loading and providing optimal amplitude of movement in the loading elements of the at least one roll in the / in those natural frequency / frequencies that cause nip pressure or nip load variation in the nip formed by the deflection compensated roll with another roll.
- Resonance is calculated and critical resonances in view of the vibration are determined and relative damping of critical resonance is maximized into certain frequency limits between 50 - 1000 Hz. Based these vibration modelling factors the deflection compensated roll is designed and damping means are designed for the at least one loading element and advantageously for the support of the roll. It should be noted that prior art design methods of calender rolls do not take into account any parameters relating to vibration or its damping and when vibration occurs in use of the calender rolls solutions are sought to dampen the vibration i.e. action is taken only after the problems occur. According to the invention the hydraulic piston of a loading element of the deflection compensated roll is separated from the loading element by resilient connection, i.e. by a disc spring, and the loading element is located in the pressure pocket of the shaft such that there is a significant tolerance between the loading element and the pressure pocket. The tolerance is 0,5 -2,5 mm, advantageously 1,0 - 2,0 mm. Furthermore this tolerance is advantageously not sealed and the loading element floats in the medium, advantageously in oil. By separation of the piston from the loading element the flow of the medium into the unsealed space is prevented and thus large flows are avoided. For providing guide of positioning the loading element in the pressure pocket the cross section of the element deviates from circular form, for example it may have grooves for providing cross-sectional flow area.
- When the loading element is under vibration it moves the medium in the volume between the piston and the loading element, which medium is pressurized and forced to flow in the tolerance of the pressure pocket of the loading element. In the tolerance the medium flow creates pressure loss that is in direct relationship with movement velocity of the loading element and thus functions as a viscous damper.
- The deflection compensated roll comprises a resilient element, which is a disc spring which is located between the piston of the at least one loading element of the roll and support of the at least one loading element is provided freely movable in the loading direction of the at least one loading element.
- Advantageously the hydraulic piston of the loading element may also be loaded by a high pressure gas volume, which will be significantly more compressible than oil. A separate oil feed line is arranged for the lubrication of the loading element.
- Leakage free air loaded zones of the roll also make it possible to use simple and compact solenoid valves for pressure control of the loading zones. Complicated servo/proportional valves are not needed, but instead pressure is controlled by adjusting the opening and closing times of the solenoid valves. Such control is known as digital pressure control.
- When the shell of the deflection compensated roll vibrates, at least one loading element moves with the shell as only thin foil of medium is between the shell and the loading element. In case the loading element moves towards the shaft of the roll, it causes a medium flow into the tolerance with high flow speed due to the narrowness of the tolerance and a flow loss is caused. The flow loss is dependent on viscosity of the medium, dimensions of the tolerance and thus at a certain movement speed a pressure loss is created which is dependent on the cross-sectional flow area of the tolerance and by this the damping force is created.
- When designing the deflection compensated roll by means of vibration modelling the optimum damping design can be calculated such that the vibration damping by loading elements will provide its maximum under different vibrations. The vibration damping can further be influenced during operating the calender, as damping is dependent from the viscosity of the medium and adjustment of viscosity of the medium is provided by adjusting the temperature of the medium and thus also adaptive vibration damping can be achieved.
- Advantageously the stiffness of the loading elements is in the range of 1 x 105 N/m - 1 x 107 N/m and damping is the range of 1 x 105 Ns/m - 1 x 106 Ns/m. The roll support stiffness is advantageously 1 x 107 N/m -5 x 108 N/m. The roll support damping is advantageously 5 x 105 Ns/m -5 x 107 Ns/m.
- According to an advantageous feature of the invention by the dimensions of the tolerance the desired damping properties are designed to the roll.
- The deflection compensated roll is designed for a roll nip of a calender such that total damping is maximized by taking into account all resonances in the roll causing pressure variations in the nip area.
- According to a further advantageous aspect the deflection compensated roll is supported by its shaft ends to the frame of the by resilient support and by a bearing. Thus a vibration damping support of the roll is provided by liquid film damping, i.e. squeeze film damping. According to this advantageous aspect when the shaft of the roll moves oil in a tolerance of a bearing housing, the oil film in the tolerance is squeezed between hard surfaces and forced to flow in the narrow gap volume. Pressure loss in the flow creates an opposite force and damping is achieved. Damping force is dependent on viscosity of the liquid, height of the tolerance and width of the shaft and the liquid film sector dimensions.
- According to an advantageous aspect support of the deflection compensated roll is provided by construction the bearings of the roll on support of a separate bushing which is supported in the loading direction to the respective bearing house by pressure pockets. The pressure pockets are filled for supporting the load pressurized gas, for example air, which has high compressibility. The area and volume of the pressure pocket is designed to provide desired compliance of the support. According to an advantageous feature perpendicular to the loading direction are additionally provided liquid pockets that are filled with oil or other liquid. The tolerance between the liquid pockets and the bushing and the sector covered by the liquid pockets and the area of the liquid pockets give the different factors to design the liquid volume such that desired viscous damping is provided. The support arrangement can also be fitted in the fixing points of calender loading cylinders.
- The damping is provided such that when the bushing moves in loading direction at the other end of the liquid volume the tolerance decreases and at the other end the tolerance increases. As the liquid flows in the narrow tolerance according to the replacement volume pressure loss is created in the flow and thus an opposing force to the movement is provided. By the advantageous aspect of the invention the stiffness and damping properties of the support of the deflection compensated roll are designed.
- According to a further advantageous aspect the deflection compensated roll is loaded in the calender by loading cylinders provided with resilient support. Thus vibrations damping support is provided by liquid film damping, i.e. squeeze film damping, in which in loading direction the force is carried by a high pressurized gas pocket and the shaft of the loading cylinder is "floating" on a small tolerance defined by discharge amount and throttling of the inlet side.
- In the following the invention is explained in detail with reference to the accompanying drawing to which the invention is not to be narrowly limited.
- In
figure 1 is shown schematically an example of the invention. - In
figure 2A is shown schematically an example of an advantageous loading element according to the invention. - In
figure 2B is shown schematically another example of a loading element which example does not fall under the scope of the claims. - In
figure 3 is shown schematically an example of an advantageous bearing arrangement according to an advantageous feature of invention. - In
figure 4 is shown schematically in further detail the liquid flow in liquid pockets of the example offigure 3 . - In
figure 5 is shown schematically another example of an advantageous bearing arrangement according to an advantageous feature of invention. - In
figures 6 and 7 are schematically shown an example of schematic example a swimming roll. - In
figures 8A - 8B is shown schematically an example the loading cylinder support of the calender. - During the course of the following description like numbers and signs will be used to identify like elements according to the different views which illustrate the invention and its advantageous examples.
- In the example of
figure 1 a nip N, for example a calender nip, is formed between a deflection compensatedroll 10 and itscounter roll 11. Thecounter roll 11 is supported by its shaft ends 13 by avibration damping element 15 and by aspring element 17 to the frame structure of the device, for example the calender. Correspondingly the deflection compensatedroll 10 is supported by its shaft ends 12 by avibration damping element 14 and by aspring element 16 to the frame structure of the device for example the calender. On theshaft 12A of the deflection compensatedroll 10 are supportedloading elements 20 of which only one is marked by reference numeral for clarity reasons. Theloading elements 20 load theshell 10A of the roll in the nip direction, as shown in the figure, i.e. towards thecounter roll 11 of the deflection compensatedroll 10. Eachloading element 20 is also provided with a dampingelement 24 and aspring element 26. - When designing the deflection compensated roll by means of vibration modelling the optimum damping design can be calculated such that in vibration modes the vibration damping by loading elements is maximized. The vibration damping can further be influenced during operating the calender, as damping is dependent from the viscosity of the medium and adjustment of viscosity of the medium is provided by adjusting the temperature of the medium and thus also adaptive vibration damping can be achieved.
- In
figure 2A is the example of theloading element 20 loads theshell 10A and it is located in a pressure pocket of theshaft 12A of the deflection compensated roll10. Theloading element 20 comprises aloading shoe 23, which hasoil pockets 25 for lubricating medium, for example oil. The lubricating medium is passed to the oil pockets 25 viachannels 27. Thehydraulic piston 21 is separated from theloading element 20 by theresilient spring element 26, by a disc spring and seals 35 seal theloading pressure pocket 33 of thepiston 21. Theloading element 20 is located in thepressure pocket 33 of theshaft 12A such that there is asignificant tolerance 31 between theloading element 20 and the pressure pocket. The tolerance is 0,5 - 2,5 mm, advantageously 1,0 - 2,0 mm. Furthermore theloading element 20 floats in the medium, advantageously in oil. For providing guide of positioning theloading element 20 in thepressure pocket 33 the cross section of the element deviates from circular form, for example it may have grooves for providing cross-sectional flow area (not shown). Below thespring element 26 is thepiston 21 that provides the loading force for theloading element 20, as shown by arrows. Thepiston 21 is sealed in thepressure pocket 33 byseals 35. - The
hydraulic piston 21 of theloading element 20 may also be loaded by a high pressure gas volume in loadingpocket 33 sealed byseals 35 as shown infigure 2B . Theloading element 20 comprises aloading shoe 23, which hasoil pockets 25 for lubricating medium, for example oil. A separateoil feed line 38 is arranged for the lubrication of theloading element 20. Thepiston 21 of theloading element 20 of is separated from theloading element 20 by thegas space 39 sealed byseals loading element 20 is located in thepressure pocket 33 of theshaft 12A such that there is asignificant tolerance 31 between theloading element 20 and the pressure pocket. The tolerance is 0,5 - 2,5 mm, advantageously 1,0 - 2,0 mm. With reference tofigures 1 and2A - 2B a deflection compensatedroll 10 comprises ashell 10A around theloading shaft 12A with loading zones provides by theloading elements 20pistons 21. The loading zones are connected to theshell 10A of theroll 10 rigidly, since thicknesses of lubricating oil between theloading elements 20 and theshell 10A are thin. Theloading elements 20 are supported on theloading shaft 12A by means of a pressure medium volume. The loading and vibration damping is provided such that when theshell 10A of the deflection compensatedroll 10 vibrates the at least oneloading element 20 moves with theshell 10A as only thin foil of medium is between theshell 10A and theloading shoe 23 of theloading element 20. In case theloading element 20 moves towards theshaft 12A of theroll 10 and it causes a medium flow into thetolerance 31 with high flow speed due to the narrowness of thetolerance 31 and a flow loss is caused. The flow loss is dependent on viscosity of the medium, dimensions of the tolerance and thus at a certain movement speed a pressure loss is created which is dependent on the cross-sectional flow area of the tolerance and by this the damping force is created. - In
figure 3 is shown a schematic example of theshaft end 12 bearinghouse 41, in which around bearing 43 an oil film is provided in tolerance i.e.liquid pocket 45 between the bearing 43 and the bearinghouse 41. The loading direction is marked by arrow LD. Pressure pockets 47 are provided in the loading direction LD.Seals 49 are located between the pressure pockets 47 and liquid pockets 45. - As shown in
figure 4 when movement L occurs in loading direction LD at the other end of theliquid pocket 45 the width decreases and at the other end the width increases. As the liquid flows in the narrowliquid pocket 45 according to the replacement volume pressure loss is created in the flow FL and thus an opposing force F to the movement is provided as indicated by dashed arrows and which provide the damping. - As shown schematically in
figure 5 the support of the shaft ends 12 of theroll 10 has aseparate bushing 50 which is supported in the loading direction LD to therespective bearing house 41 by pressure pockets 47. The pressure pockets 47 are filled with pressurized gas, for example air, which high compressibility. The area and volume of thepressure pocket 47 is designed to provide desired compliance of the support. Perpendicular to the loading direction LD is additionally providedliquid pockets 45 that are filled with oil or other liquid. The tolerance between theliquid pockets 45 and thebushing 50 and sector covered by the liquid pockets 45 and area of the liquid pockets 45 give the different factors to design the liquid volume such that desired viscous damping is provided. The damping is provided such that when thebushing 50 moves in loading direction LD at the other end of the liquid volume the tolerance decreases and at the other end the tolerance increases. As the liquid flows in the narrow tolerance according to the replacement volume pressure loss is created in the flow and thus an opposing force to the movement is provided. According to the schematic example presented infigure 6 and 7 aswimming roll 60 is provided by a spring (not shown) in theloading element 62, which loading element is similar tofigure 2 . When theshell 65 of theroll 60 moves due to vibration the spring follows theshell 65 and thus compensates the movement and vibration damping is provided. - In
figures 8A - 8B is shown schematically an example theloading cylinder support 70 of the calender, with resilient support. Thus vibrations damping support is provided by liquid film damping, i.e. squeeze film damping, in which in loading direction the force is carried by a highpressurized gas pocket 71, which corresponds to pressurepocket 47 offigures 3 and5 and the shaft of the loading cylinder is "floating" on a small tolerance defined by discharge amount and throttling of the inlet side. Acone structure 72 provides the positioning of the shaft of the loading cylinder and functional tolerances are provided by axial tightening means 73. In direction perpendicular to the loading the shaft positions byhydraulic pockets 74, in which oil is fed into middle of the pockets and discharged from edge grooves of the pockets and operation of which corresponds to that ofliquid pockets 45 offigures 3 - 5 .Hydraulic pockets 74 also provide viscous dampening by squeeze film effect.
Claims (2)
- Deflection compensated roll for a fiber web machine, in particular for a calender, which roll (10) comprises a shaft (12A) and shaft ends (12), a shell (10A) and at least one loading element (20) loading the shell (10A) and located in pressure pockets (33) of the shaft (12A), which roll (10) is a nip roll, said deflection compensated roll (10) comprising damping means (24, 26) for said at least one loading element (20) of the deflection compensated roll (10) for damping vibration of the shell (10A) of the roll, which damping means comprise a spring element (26) and a damping element (24), wherein said at least one loading element (20) is freely movable in the loading direction, wherein the loading element (20) and a piston (21) for moving the loading element (21) are located in the pressure pocket (33) and the spring element is a disc spring and located in the pressure pocket (33) between the loading element (20) and the piston (21) and the pressure pocket (33) comprises medium in which the loading element (20) floats, and the damping element (24) is provided as a viscous damper by a tolerance (31) between the loading element (20) and the pressure pocket (33) characterized in that the tolerance (31) is 0,5 - 2,5 mm, advantageously 1,0 - 2,0 mm, and comprises the medium and when the loading element (20) is under vibration due to vibration of the roll shell (10A) the medium moves in the pressure pocket (33) towards the tolerance (31) and in the tolerance (31) the medium flow creates pressure loss that is in direct relationship with movement velocity of the loading element (20).
- Deflection compensated roll according to claim 1, characterized in that the tolerance (31) is unsealed.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP13169860.7A EP2808445B1 (en) | 2013-05-30 | 2013-05-30 | Deflection compensated roll |
CN201420282184.0U CN204059089U (en) | 2013-05-30 | 2014-05-29 | The migration roller of fiber web machine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP13169860.7A EP2808445B1 (en) | 2013-05-30 | 2013-05-30 | Deflection compensated roll |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2808445A1 EP2808445A1 (en) | 2014-12-03 |
EP2808445B1 true EP2808445B1 (en) | 2017-03-15 |
Family
ID=48520801
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13169860.7A Active EP2808445B1 (en) | 2013-05-30 | 2013-05-30 | Deflection compensated roll |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP2808445B1 (en) |
CN (1) | CN204059089U (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FI127119B (en) | 2015-10-27 | 2017-11-30 | Valmet Technologies Oy | A system for damping vibrations in the nip of a fiber web machine |
CN106904476B (en) * | 2017-05-05 | 2018-06-29 | 郑端金 | A kind of cloth conveying automatic correcting mechanism |
CN106904474B (en) * | 2017-05-05 | 2018-05-25 | 佛山市南海区金龙恒家具有限公司 | One kind has automatic lifting cloth conveying automatic correcting mechanism |
CN106946079B (en) * | 2017-05-05 | 2018-06-22 | 东莞市鑫盛手袋工艺有限公司 | A kind of cloth conveying cutting mechanism with automatic correcting mechanism |
CN108265430A (en) * | 2018-03-06 | 2018-07-10 | 东莞市坚华机械有限公司 | A kind of novel single Woven tape dyeing machine |
EP3617403B1 (en) * | 2018-08-30 | 2021-09-01 | Valmet Technologies Oy | Method of treating a fiber web and a treatment system for treatment of a fiber web |
CN113862927B (en) * | 2021-09-06 | 2023-11-03 | 海宁忆丹纺织股份有限公司 | Finishing device for decorative fabric |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10248519B4 (en) | 2002-10-17 | 2006-11-02 | Voith Patent Gmbh | Center roller of a calender and calender |
FI118056B (en) * | 2004-11-11 | 2007-06-15 | Metso Paper Inc | Arrangement for damping the vibrations of a deflection compensated roll |
FI118812B (en) * | 2006-02-01 | 2008-03-31 | Metso Paper Inc | Method for Controlling the Specific Vibration Frequency of a Calender Intermediate Roll and Vibration Dampener |
US20080000363A1 (en) * | 2006-06-29 | 2008-01-03 | Metso Paper, Inc. | Adjustable Anti-Barring Device for Calender Rolls |
FI121752B (en) * | 2009-07-07 | 2011-03-31 | Metso Paper Inc | Apparatus and method for controlling the runnability of a fiber web handling nip |
DE102010002503A1 (en) * | 2010-03-02 | 2011-09-08 | Voith Patent Gmbh | Roller for a paper or board machine and method for damping vibrations of a roller |
DE102010039795A1 (en) * | 2010-08-26 | 2012-03-01 | Voith Patent Gmbh | Apparatus and method for reducing vibration on a bending roll |
-
2013
- 2013-05-30 EP EP13169860.7A patent/EP2808445B1/en active Active
-
2014
- 2014-05-29 CN CN201420282184.0U patent/CN204059089U/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
CN204059089U (en) | 2014-12-31 |
EP2808445A1 (en) | 2014-12-03 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2808445B1 (en) | Deflection compensated roll | |
CA1302762C (en) | Vibration-absorber | |
EP2013412B1 (en) | Support body for an apparatus having an extended nip for the treatment of a fibre web | |
FI122329B (en) | Bending-compensated roller for paper / cardboard or finishing machine | |
WO2004044316A1 (en) | A method and an arrangement for controlling position and/or force of an elongated rolling device | |
US5024150A (en) | Process for reducing vibrations of successive sets of rolls and a roll arrangement having reduced vibratory tendencies | |
EP1678374B1 (en) | Support body, holding device therefor, apparatus with said body for treatment of a web, methods of forming an extended nip in the apparatus and controlling load in the nip | |
EP2737125A1 (en) | A paper making machine for making tissue paper and a method of operating a paper making machine | |
FI115554B (en) | Plant for supporting a roll in a paper, cardboard, or finishing machine and method for controlling the boom of a roll | |
FI120409B (en) | Bending-compensated roller for a fiber web or finishing machine, method of driving and manufacturing a bending-compensated roller and apparatus for damping oscillations in a hydraulic pressure medium | |
JPH04308295A (en) | Wire for fiber pulp web and felt guide apparatus | |
US20080000363A1 (en) | Adjustable Anti-Barring Device for Calender Rolls | |
FI119519B (en) | Drum and vibration damper for a paper machine | |
US20070060456A1 (en) | Roll for pressure treatment of material bands | |
EP2722437B1 (en) | Web pressing and dewatering method and pressing apparatus for a paper- or board-making machine | |
FI121752B (en) | Apparatus and method for controlling the runnability of a fiber web handling nip | |
US7300549B2 (en) | Method for controlling the operation of a paper, board or tissue production line | |
EP2669430A1 (en) | Arrangement for controlling vibrations in a fiber web machine | |
KR20060124585A (en) | Shoe press mechanism of paper machine | |
WO2007110488A1 (en) | Control valve | |
EP2754750A1 (en) | Arrangement for controlling vibrations in a fiber web machine and a linear motion amplifier | |
CN102959257A (en) | Roller and method for avoiding its vibrations | |
FI104648B (en) | Method and device for modifying the eigen frequency of a roll nip structure in a paper or cardboard machine | |
EP2483474B1 (en) | Hydraulic actuator, method and apparatus for dampening vibration of a machine element | |
FI117301B (en) | Storage of a web processing machine's roller and method of damping the roll vibration |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20130530 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
AX | Request for extension of the european patent |
Extension state: BA ME |
|
R17P | Request for examination filed (corrected) |
Effective date: 20150506 |
|
RBV | Designated contracting states (corrected) |
Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
17Q | First examination report despatched |
Effective date: 20160426 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20161014 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 875702 Country of ref document: AT Kind code of ref document: T Effective date: 20170415 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602013018486 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20170315 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170616 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170615 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 875702 Country of ref document: AT Kind code of ref document: T Effective date: 20170315 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170531 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170615 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170715 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170717 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602013018486 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 |
|
26N | No opposition filed |
Effective date: 20171218 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20170615 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170531 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170531 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20180131 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170530 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20170531 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170615 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170530 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170531 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170531 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170530 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20130530 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20170315 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20240521 Year of fee payment: 12 |