WO2021043553A1 - Procédé de surveillance d'éléments d'étanchéité d'un ensemble cylindre à actionnement fluidique et ensemble cylindre - Google Patents

Procédé de surveillance d'éléments d'étanchéité d'un ensemble cylindre à actionnement fluidique et ensemble cylindre Download PDF

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Publication number
WO2021043553A1
WO2021043553A1 PCT/EP2020/072610 EP2020072610W WO2021043553A1 WO 2021043553 A1 WO2021043553 A1 WO 2021043553A1 EP 2020072610 W EP2020072610 W EP 2020072610W WO 2021043553 A1 WO2021043553 A1 WO 2021043553A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
roller
valve
actuating fluid
pressure chamber
Prior art date
Application number
PCT/EP2020/072610
Other languages
German (de)
English (en)
Inventor
Andre Hünnekens
Original Assignee
Andritz Küsters Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Andritz Küsters Gmbh filed Critical Andritz Küsters Gmbh
Priority to CN202080062518.1A priority Critical patent/CN114599952A/zh
Publication of WO2021043553A1 publication Critical patent/WO2021043553A1/fr

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/005—Sealing rings
    • 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
    • D21G1/022—Controlled deflection rolls with deflection compensation means acting between the roller shell and its supporting member the means using fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • F16C13/022—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle
    • F16C13/024—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle
    • F16C13/026—Bearings supporting a hollow roll mantle rotating with respect to a yoke or axle adjustable for positioning, e.g. radial movable bearings for controlling the deflection along the length of the roll mantle by fluid pressure
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M3/00—Investigating fluid-tightness of structures
    • G01M3/02—Investigating fluid-tightness of structures by using fluid or vacuum
    • G01M3/26—Investigating fluid-tightness of structures by using fluid or vacuum by measuring rate of loss or gain of fluid, e.g. by pressure-responsive devices, by flow detectors

Definitions

  • the invention relates to a method for monitoring sealing elements of a fluidically actuated roller, in which the sealing elements are acted upon by a pressurized actuating fluid, the pressure of the actuating fluid being influenced by means of a pressure valve.
  • the invention further relates to a fluidically actuated roller with an internal stroke and / or deflection compensation, comprising at least one fluidic support element having sealing elements and / or at least one pressure chamber having the sealing elements, as well as at least one pressure valve, with which the pressure, with the at least one Support element and / or at least one pressure chamber is acted upon, can be influenced.
  • Fluidically operated rollers with an internal stroke and / or a deflection compensation are regularly provided with dynamic sealing elements in the interior of the roller.
  • compressed gases or pressurized liquids, in particular hydraulic fluid can be used to provide the fluidic pressure.
  • Thermal oils are also used for heated, deflection-controllable rollers.
  • Rollers of this type with an internal stroke and / or deflection compensation are regularly known as so-called “punch-supported rolls” or as so-called “floating They regularly comprise a stationary carrier on which a roller shell is rotatably mounted.
  • a plurality of support elements which are radially guided on the carrier and designed in the manner of a piston / cylinder unit, are regularly distributed over the length of the carrier.
  • the dynamic sealing elements are formed by piston seals which seal the piston in the cylinder space provided for receiving it in the carrier against the exit of the actuating fluid supplied to it.
  • Such a roller is known, for example, from DE 295 03 126 Ul.
  • a pressure chamber is regularly provided between the carrier and the roller shell, which is acted upon by the actuating fluid so that a hydraulic support force can be transmitted from the carrier to the shell.
  • This pressure chamber hereinafter also referred to as the "first pressure chamber”
  • a leakage chamber hereinafter also referred to as the "second pressure chamber”
  • longitudinal and front seals form the dynamic sealing elements.
  • Such a roller is known, for example, from WO 2004/097110 A1.
  • the heat transfer fluid - usually the actuating fluid - has to be drained off at regular intervals. Aids such as tools, transport equipment, etc. Devices and a replacement roller must first be provided. The sudden occurrence of unforeseen leaks is therefore regularly associated with long downtimes and production losses.
  • the pressurized actuation fluid can be applied to such rollers in different ways:
  • Pressure regulation in advance Here, an already regulated pressure is supplied to the cylinder spaces of the punch-supported roller or the first pressure chamber of the floating roller.
  • the leakage regularly corresponds to the sum of the leakages on the Kol bendichtung and the leakage between the support elements and the roller tube.
  • the leakage usually corresponds to the sum of the leakages at the front and longitudinal seals of the pressure chamber.
  • the pressures can be regulated in particular via various valves. Proportional valves may first be mentioned as an example. If these are used, the oil pressure is measured, the recorded actual value is compared with a given setpoint, and the actual / setpoint difference is applied to a control module for controlling the proportional valves.
  • This control module changes the control signal for the proportional valve on the basis of the difference (also referred to as control deviation). If, for example, pneumatic pressure regulators are used, an air pressure is determined from the detected actual / target value difference by a machine control, which is provided by an IP converter and fed to the pneumatic pressure regulator.
  • Pressure control in the return line In the case of heated, floating rollers in particular, pressure control in the return line from the first pressure chamber has proven itself.
  • a volume flow of actuating fluid that is as constant as possible, for example provided by a hydraulic pump, is first fed to the first pressure chamber, then flows through it, then a pressure valve, via which a pressure which can be set directly or indirectly, and finally the second pressure chamber, also known as a "leakage chamber"
  • a valve can basically be any component that is suitable for creating a pressure drop by changing a throttle cross-section. witness.
  • This valve is particularly preferably a pneumatically operated pressure regulator which balances a pneumatic pressure, which can be predetermined by a machine control system, for the pressure drop in the volume flow of the roller.
  • This pressure regulator is also referred to in the following as a “differential pressure regulator”.
  • corresponding pressure regulation is also used in so-called “CS rollers”. These have two first pressure chambers, each of which has a flow and a return. Each return leads through a pressure valve. The actuating fluid flowing back from the pressure valve is combined with a possible leakage flow.
  • the invention is based on the object of creating measures by the application of which the risk of an unexpected failure of the roller due to a sudden loss of pressure is substantially reduced.
  • the volume flow of the actuating fluid is detected directly by the pressure valve, or a variable is measured from which the volume flow of the actuating fluid through the pressure valve can be inferred.
  • the volume flow or this variable is recorded continuously or at specific, predetermined time intervals.
  • the state of the sealing elements is deduced from the time course of the recorded volume flow.
  • pressure control in the flow an increase in the volume flow, in the case of pressure control in the return, a decrease in the volume flow as an indication of increasing leakage, and that an overhaul of the roller or its sealing elements should be planned.
  • the inventive detection of the volume flow of the actuating fluid ids can be determined by the pressure valve, whether the error is in the ready position of the pressurized actuating fluid (for example, the function of a pressure regulator, a pump, etc. is disturbed). In this case, no or only an unexpectedly low volume flow would be recorded. Or whether damaged sealing elements are responsible for the pressure not being built up. In this case, an unexpectedly high volume flow would be recorded in the case of pressure control in the flow, and an unexpectedly low volume flow in the case of pressure control in the return.
  • Troubleshooting could include first determining whether the differential pressure regulator is working, or e.g. B. an incorrect control pressure is provided, or there is a mechanical error in the controller. This could be recognized by the displacement transducer, for example, from the fact that the valve is not moving at all or is in contact with an end stop.
  • the volume flow to the hydraulic support elements of a stamp-supported roller or to the first pressure chamber of a floating roller can be recorded directly, for example, by means of a flow sensor.
  • the flow sensor can be switched into a feed line for the actuating fluid.
  • valve position of the pressure valve it is also possible to monitor the valve position of the pressure valve and to deduce the volume flow from the valve position.
  • the valve position can be observed or converted into an evaluation variable that is proportional to the volume flow.
  • the volume flow of the actuating fluid is regularly first fed to a first pressure chamber of the roller, then to the pressure valve and finally to a second pressure chamber of the roller (also known as the leakage chamber), a pressure difference being set between the first and second pressure chambers by means of the pressure valve. Since an almost constant volume flow of the actuating fluid is usually supplied to the roller, the valve position in the return can be detected in order to detect the increase in leakage between the first and second pressure chambers, which indicates increased wear of sealing elements. If this valve closes to maintain the required pressure difference, it can be concluded that the internal leakage has increased.
  • the pressure difference in the first and second pressure chambers is dependent on a valve lift of the pressure valve, to measure the valve lift and compare it with a predetermined valve lift. An unexpected difference can in turn indicate an increase in leakage between the first and second pressure chambers and that sealing elements are worn.
  • the volume flow of the actuating fluid into the cylinder spaces or the first or first pressure chambers is measured.
  • the volume flow from the first pressure chamber or chambers is measured.
  • the fluidically actuated roller with internal stroke and / or deflection compensation the at least one fluidic support element having sealing elements and / or at least one pressure chamber having sealing elements and at least one pressure valve with which the pressure, with the at least one support element and / or at least one pressure chamber is acted upon, can be influenced, comprises according to the invention means with which a volume flow of actuating fluid flowing through the pressure valve can be detected. On the basis of the detection of the volume flow, a comparison with reference values that are stored, for example, in an electronic data memory, allows conclusions to be drawn about progressive wear of sealing elements.
  • the means with which the volume flow of actuating fluid flowing through the pressure valve can be detected preferably comprise at least one flow meter.
  • the means with which the volumetric flow of actuating fluid flowing through the pressure valve can be detected can comprise a measuring device for a measured variable from which the volumetric flow of the actuating fluid can be inferred.
  • the fluidically actuated roller according to the invention preferably comprises a first and a second pressure chamber and is designed in such a way that initially the first and then the second pressure chamber is traversed by the actuating fluid.
  • the pressure valve is preferably designed as a differential pressure regulator, which has the effect that the actuating fluid is supplied to the first pressure chamber at a higher pressure than the second pressure chamber (also referred to as the "leakage chamber").
  • the differential pressure regulator preferably comprises a valve body that can be displaced from a closed position The distance displaced from the closed position is referred to as the valve lift.
  • the roller then preferably also comprises a differential pressure measuring device which detects the difference between the fluid pressures prevailing in the first and second pressure chambers.
  • a displacement transducer is provided that detects the valve lift. If the valve lift changes in order to maintain the pressure difference of the actuating fluid in the first and in the second pressure chamber, this can indicate a change in the leakage and, as a result, the state of the sealing elements can be deduced.
  • such a roller can comprise a flow meter with which the volume flow of the actuating fluid into the first or the first pressure chambers can be detected directly and / or can be detected through the second pressure chamber. An increase in the measured flow indicates a progressive wear of the sealing elements. If the roller has a flow meter with which the volume flow from the first pressure chamber can be recorded, a decrease in the measured flow indicates progressive wear of sealing elements.
  • the flow meter can - as is particularly preferred - comprise a Venturi nozzle, a measuring orifice, a standard nozzle and / or a pitot tube and be integrated in a suitable manner into or connected to a line through which the actuating fluid flows.
  • FIG. 1 shows a two-roll calender with a roll belonging to the prior art, the latter shown partially in section;
  • Fig. 2 shows a portion of a first embodiment of a roller according to the Invention, again shown partially in section;
  • FIG. 3 shows a second exemplary embodiment of a roller according to the invention in a representation corresponding to FIG. 2, and also
  • FIG. 4 shows a representation corresponding to FIG. 1 of a two-roll calender with a third exemplary embodiment of a roll according to the invention.
  • the calender designated as a whole by Kl in FIG. 1 comprises a calender frame 1 in which a roller 2 is rotatably mounted about an axis A1 via roller bearings 3.
  • the calender Kl also includes a roller 4, which is designed as a floating roller. It comprises a non-rotatably mounted carrier 5, which can be displaced on the calender frame via Hubzy cylinder 6 to and from roller 2
  • the roller 4 also comprises a roller jacket 7 which is mounted on the carrier 5 via roller bearings 8 so that it can rotate about an axis A2.
  • a nip 9 through which a web of material, for example made of paper, fleece, textile or film, is passed through for treatment thereof.
  • the roller 4 is a so-called “floating roller”. It comprises a first pressure chamber 10 which is formed on the side facing the other roller 2 between the carrier 5 and the roller shell 7.
  • the first pressure chamber is opposite a second pressure chamber 13 via sealing elements designed as longitudinal seals 11 and end seals 12, also called “leakage chamber”, sealed.
  • the carrier 5 has first channels 14, which open into the first pressure chamber 10 from both front sides, and second channels 15, which open from the front sides into the second pressure chamber 13.
  • a hydraulic pump P is provided which is connected via a supply line 16 to the first channel 14 shown on the right in FIG. 1. It is used to drive an actuating fluid, for example a hydraulic oil, to the first pressure chamber 10 with a constant volume flow. From the pressure chamber 10 GE reaches the actuating fluid via the first channel 14 shown in the drawing on the left to a differential pressure regulator 17 formed pressure valve and from this to the second channel 15 shown in Fig. 1 on the left. Through this, the actuating fluid is fed to the second pressure chamber 13 and arrives from this via the second channel 15 on the right in FIG. 1 and a line 18 into a pressureless reservoir R of the actuating fluid.
  • an actuating fluid for example a hydraulic oil
  • the differential pressure regulator 17 causes a pressure drop in the actuating fluid flowing through it, so that the actuating fluid in the first pressure chamber 10 is at a higher pressure than in the second pressure chamber 13.
  • the pressure difference specified by the differential pressure regulator 17 is selected so that that in the first pressure chamber 10 of in NEN acting on the roll shell 7 pressure leads to the fact that on the roll shell 7 to the carrier 5 directed weight and line forces from the roll zenspalt and a deflection of the roll 2 are compensated, so that the roll gap 9 over its length a has at least substantially constant gap height.
  • the differential pressure regulator 17 is controlled pneumatically.
  • the height of the applied pneumatic control pressure PS is a measure of the setpoint of the desired differential pressure between the first pressure chamber 10 and the second pressure chamber 13.
  • the control pressure PS is specified by the machine control PLC when the roller 4 is in operation.
  • the pressure with which the lifting cylinders 6 are acted upon during operation is also provided by the machine control PLC, so that the line force prevailing in the nip 9 can be set to a desired value.
  • the exemplary embodiment of the roller 4 shown in FIG. 1 furthermore comprises a differential pressure meter 50 with which the differential pressure value Pdiff falling at the differential pressure regulator 17 is recorded. An unexpected drop in the actual differential pressure value suggests that more actuating fluid is getting from the first pressure chamber 10 into the second pressure chamber 13, bypassing the differential pressure regulator 17, and can mean a total failure of sealing elements, which may require the calender to be shut down immediately.
  • FIG. 2 an exemplary embodiment of a roller 19 further developed according to the invention is partially shown.
  • the roller 19 is, in turn, a floating roller with a non-rotatably mounted carrier 20 and a roller jacket 21 rotatably mounted about it.
  • the roller jacket 21 is mounted on the carrier 20 on the outside.
  • a bearing dome 22 is arranged on the carrier 20, which encompasses an area of enlarged diameter 23.
  • a roller bearing 24 is provided in the area 23, which acts from the outside on an area 25 of smaller diameter of the roller shell 21.
  • the roller 19 in turn comprises a first pressure chamber 26 and a second pressure chamber 27, also called a leakage chamber.
  • the first and second pressure chambers 26, 27 are in turn formed between the carrier 20 and the roll shell 21 and are separated from one another by means of longitudinal seals 28 and end seals 29 comprising de sealing elements.
  • Fig. 2 only a left area of this roller, on which a differential pressure regulator 30 is provided, is shown. It goes without saying that the right-hand area of the roller 19, which is not shown in the drawing, can be configured in a corresponding manner and mounted on the outside of the carrier. Only a differential pressure regulator is not provided, but rather actuating fluid is fed to the first pressure chamber 26 and discharged from the second pressure chamber 27, for example as described in relation to FIG. 1.
  • the differential pressure regulator 30 comprises a valve body 31 which comprises a first valve disk 32, a second valve disk 33 and a connecting component 34 connecting the two valve disks 32, 33 to one another.
  • the first valve disk 32 is arranged in a pneumatic cylinder 35 to which a control pressure PS acting on the first valve disk 32 can be applied.
  • the pneumatic pressure causes the Ven til stresses 31 to the right pressing force.
  • the valve body 31 is arranged to be displaceable relative to the carrier 20 and the bearing dome 22 in the longitudinal direction of its connecting component 34.
  • a channel 36 which opens into the first pressure chamber 26 and is present in the actuating fluid with the pressure PD prevailing in the pressure chamber 26.
  • the channel 36 opens at its other end into a hydraulic pressure chamber 37 which can be closed or released by the second valve disk 33.
  • the hydraulic chamber 37 is fluidically connected to return ducts 38 which open into the second pressure chamber 27.
  • Valve body 31, pneumatic cylinder 35 and hydraulic pressure chamber 37 are designed in such a way that the second valve disk 33 closes the hydraulic pressure chamber 37 to the outside, in particular with respect to the return ducts 38, when the force acting on the second valve disk 33 through the hydraulic pressure PD in the first pressure chamber 26 is smaller than the force acting on the first valve disk 32 due to the pneumatic control pressure PS. If now - as in the embodiment shown in FIG. 1 - actuating fluid is fed to the first pressure chamber 26, for example with a constant volume flow, a hydraulic pressure will build up in the first pressure chamber 26 and thus in the hydraulic pressure chamber 37, which increases until the Valve body
  • a position transducer 39 is provided in the embodiment of a roller according to the invention shown in FIG. 2, with which the valve stroke H or the respective position of the Ventilkör pers 31 can be detected.
  • the functional principle of the transducer 39 can be inductive, for example, its actuator can be employed by a spring.
  • Its output signal HS which characterizes the respective valve lift, can accordingly also be analog, for example as a current in the milliamperes range, the level of which depends on the valve lift.
  • a second exemplary embodiment of a roller according to the invention is shown in a representation corresponding to FIG. 2 in FIG. 3.
  • the differences between the second embodiment and the first embodiment will be reproduced, for example.
  • the same reference symbols denote corresponding components.
  • a flow meter 51 is provided, which comprises a cross-section reduction in the form of a Venturi nozzle 41 in the channel 36. The resulting pressure difference from the pressure in the non-tapered channel PA / PB due to the tapering of the cross-section is measured, as a result of which the volume flow V through the channel 36 can be detected.
  • FIG. 4 in a representation corresponding to FIG. 1, a calender K2 with a fourth embodiment of a roll 42 according to the invention is shown.
  • the water roller 42 is a so-called punch-supported roller. It has a carrier 43 which, in a manner known per se and not shown in the drawing, carries a plurality of support elements 44 which are radially guided on the carrier 43 and are designed in the manner of a piston / cylinder unit.
  • the support elements 44 act on a roll shell 45 which is rotatably mounted on the carrier 43 via roller bearings 46.
  • each of these support elements is acted upon with actuating fluid, which is provided by a pump P.
  • the pressure PI... P8, under which each support element 44 is acted upon with actuating fluid, is set individually with the aid of a pressure valve 48 assigned to the respective support element 44.
  • the volume flows Q1... Q8 of the actuating fluid supplied to the support elements 44 are also measured with the aid of flow meters 49. From an unexpected increase it can be concluded that the sealing elements 47 of the respective support element 44 are wearing progressively.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • General Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Abstract

L'invention concerne un procédé et un cylindre à actionnement fluidique (4, 19, 42), des éléments d'étanchéité (11, 12, 28, 29, 47) étant soumis à l'action d'un fluide d'actionnement sous pression, la pression du fluide d'actionnement pouvant être réglée au moyen d'une soupape de pression (17, 30, 48), et le débit volumétrique du fluide d'actionnement étant détecté par la soupape de pression (17,30, 48) pour déterminer l'usure des éléments d'étanchéité (11, 12, 28, 29, 47).
PCT/EP2020/072610 2019-09-04 2020-08-12 Procédé de surveillance d'éléments d'étanchéité d'un ensemble cylindre à actionnement fluidique et ensemble cylindre WO2021043553A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202080062518.1A CN114599952A (zh) 2019-09-04 2020-08-12 监测流体操动式辊子装置的密封元件的方法以及辊子装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019123658.4 2019-09-04
DE102019123658.4A DE102019123658A1 (de) 2019-09-04 2019-09-04 Verfahren zur Überwachung von Dichtungselementen einer fluidisch betätigten Walzenanordnung sowie Walzenanordnung

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Publication Number Publication Date
WO2021043553A1 true WO2021043553A1 (fr) 2021-03-11

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PCT/EP2020/072610 WO2021043553A1 (fr) 2019-09-04 2020-08-12 Procédé de surveillance d'éléments d'étanchéité d'un ensemble cylindre à actionnement fluidique et ensemble cylindre

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CN (1) CN114599952A (fr)
DE (1) DE102019123658A1 (fr)
WO (1) WO2021043553A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202200011375A1 (it) * 2022-05-30 2023-11-30 Ramina S R L Macchina per la calandratura

Citations (9)

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EP0347549A2 (fr) * 1988-06-22 1989-12-27 Eduard Küsters Maschinenfabrik GmbH & Co. KG Rouleau à pression réglable le long d'une ligne
DE3941965A1 (de) * 1989-11-09 1990-05-31 Escher Wyss Ag Verfahren und vorrichtung zum walzen einer warenbahn
DE3909911C1 (fr) * 1989-03-25 1990-06-07 Kleinewefers Gmbh, 4150 Krefeld, De
EP0536501A2 (fr) * 1991-10-10 1993-04-14 J.M. Voith GmbH Rouleau à compensation de flèche
DE4225642C1 (fr) * 1992-07-02 1993-07-29 Sulzer-Escher Wyss Ag, Zuerich, Ch
DE29503126U1 (de) 1995-02-24 1996-06-20 Eduard Küsters Maschinenfabrik GmbH & Co KG, 47805 Krefeld Walze
WO2004097110A1 (fr) 2003-04-30 2004-11-11 Eduard Küsters Maschinenfabrik GmbH & Co. KG Cylindre destine au traitement de compression de bandes de materiau
US20140290750A1 (en) * 2013-04-01 2014-10-02 Schaeffler Technologies AG & Co. KG Method of determining an operating state of a transmission latching valve
US20150211379A1 (en) * 2014-01-24 2015-07-30 Solar Turbines Inc. System for monitoring health of a seal

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DE19652372A1 (de) * 1996-12-17 1998-06-18 Zinser Textilmaschinen Gmbh Pneumatische Belastungsvorrichtung eines Streckwerkes in einer Spinnmaschine
US7692553B2 (en) * 2006-07-21 2010-04-06 Deublin Company Leak detecting system for rotating union
FI123057B (fi) * 2011-06-01 2012-10-15 Metso Paper Inc Tiivistyssovitelmalla varustettu uiva tela ja menetelmä uivan telan tiivistämiseksi
DE102011052709A1 (de) * 2011-08-15 2013-02-21 Andritz Küsters Gmbh Walzenanordnung für einen Thermobonding-Kalander sowie Betriebsverfahren einer Walze
CN206339341U (zh) * 2016-12-12 2017-07-18 山东钢铁股份有限公司 一种离线检测轧辊密封漏油的检测装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0347549A2 (fr) * 1988-06-22 1989-12-27 Eduard Küsters Maschinenfabrik GmbH & Co. KG Rouleau à pression réglable le long d'une ligne
DE3909911C1 (fr) * 1989-03-25 1990-06-07 Kleinewefers Gmbh, 4150 Krefeld, De
DE3941965A1 (de) * 1989-11-09 1990-05-31 Escher Wyss Ag Verfahren und vorrichtung zum walzen einer warenbahn
EP0536501A2 (fr) * 1991-10-10 1993-04-14 J.M. Voith GmbH Rouleau à compensation de flèche
DE4225642C1 (fr) * 1992-07-02 1993-07-29 Sulzer-Escher Wyss Ag, Zuerich, Ch
DE29503126U1 (de) 1995-02-24 1996-06-20 Eduard Küsters Maschinenfabrik GmbH & Co KG, 47805 Krefeld Walze
WO2004097110A1 (fr) 2003-04-30 2004-11-11 Eduard Küsters Maschinenfabrik GmbH & Co. KG Cylindre destine au traitement de compression de bandes de materiau
US20140290750A1 (en) * 2013-04-01 2014-10-02 Schaeffler Technologies AG & Co. KG Method of determining an operating state of a transmission latching valve
US20150211379A1 (en) * 2014-01-24 2015-07-30 Solar Turbines Inc. System for monitoring health of a seal

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CN114599952A (zh) 2022-06-07

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