DK176712B1 - Duo roller machine and method for operating it. - Google Patents
Duo roller machine and method for operating it. Download PDFInfo
- Publication number
- DK176712B1 DK176712B1 DK124997A DK124997A DK176712B1 DK 176712 B1 DK176712 B1 DK 176712B1 DK 124997 A DK124997 A DK 124997A DK 124997 A DK124997 A DK 124997A DK 176712 B1 DK176712 B1 DK 176712B1
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- DK
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- Prior art keywords
- roller
- hydro
- pneumatic system
- bubble
- gas volume
- Prior art date
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B3/00—Presses characterised by the use of rotary pressing members, e.g. rollers, rings, discs
- B30B3/04—Presses characterised by the use of rotary pressing members, e.g. rollers, rings, discs co-operating with one another, e.g. with co-operating cones
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/16—Control arrangements for fluid-driven presses
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/04—Accumulators
- F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/20—Accumulator cushioning means
- F15B2201/205—Accumulator cushioning means using gas
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/30—Accumulator separating means
- F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/30—Accumulator separating means
- F15B2201/315—Accumulator separating means having flexible separating means
- F15B2201/3152—Accumulator separating means having flexible separating means the flexible separating means being bladders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/30—Accumulator separating means
- F15B2201/32—Accumulator separating means having multiple separating means, e.g. with an auxiliary piston sliding within a main piston, multiple membranes or combinations thereof
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/40—Constructional details of accumulators not otherwise provided for
- F15B2201/41—Liquid ports
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2201/00—Accumulators
- F15B2201/40—Constructional details of accumulators not otherwise provided for
- F15B2201/415—Gas ports
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
- Rolls And Other Rotary Bodies (AREA)
Description
DK 176712 B1 iDK 176712 B1 i
Opfindelsen angår en duovalsemaskine, navnlig en højtryksvalsepresse til trykbehandling af kornet gods, med to drejeligt lejrede, i modsat omløbsretning drevne og af en valsespalte fra hinanden adskilte valser, hvor 5 den ene af de to valser er udformet som en fast valse, der ved hjælp af sine lejebukke støtter direkte mod endevæggen af maskinstativet, og den anden valse er udformet som en løs valse, der ved hjælp af sine to tilhørende lejebukke støtter mod en hydraulisk cylinder 10 i et hydro-pneumatisk system - med et gasfyldt boblelager til dæmpning af pressetrykspidserne - hvor valse-pressekraften tilvejebringes med det hydro-pneumatiske system, og indstillingen af valsespaltebredden foretages med det hydro-pneumatiske system. Desuden angår 15 opfindelsen en fremgangsmåde til drift af en sådan duovalsemaskine.BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a dual-roller machine, in particular a high-pressure roller press for treating grain cargo, with two pivotally mounted, counterclockwise and spaced-apart rollers, one of the two rollers being formed by means of a fixed roller. of its bearing blocks supports directly against the end wall of the machine frame, and the second roller is formed as a loose roller, which, by means of its two associated bearing blocks, supports against a hydraulic cylinder 10 in a hydro-pneumatic system - with a gas-filled bubble bearing for damping the pressure pressures - where the roller pressing force is provided with the hydro-pneumatic system and the adjustment of the roll gap width is made with the hydro-pneumatic system. In addition, the invention relates to a method for operating such a dual roller machine.
Kendte duovalsemaskiner, såsom valsepresser eller valsemøller, har to drejeligt lejrede, modsat roterende valser, som imellem sig danner en valsespalte, hvori 20 det kornede gods trækkes ind og underkastes en trykpåvirkning - med henblik på komprimering eller findeling.Known duo roll machines, such as roller presses or roller mills, have two pivotally mounted, opposite rotating rollers which form between themselves a roller slot into which the grained material is retracted and subjected to a compressive action - for compression or comminution.
Der kendes højtryks-valsepresser til såkaldt godslejefindeling af kornet gods, såsom eksempelvis cementklinker, som i valsespalten presses med ekstremt 25 højt tryk til skælformede plader, som efterfølgende deagglomereres (brochuren "Rollenpresse" Nr. 11-304 d fra KHD Humboldt Wedag AG) , hvorved det én gang pressede gods kan udvise en stor andel af partikler, som allerede er reduceret til den ønskede finhed, eksempel-30 vis kan 25% være mindre end 90 μιη. Dette høje tryk, som i valsespalten indvirker på det kornede gods, og som ved forskydning af den løse valse ville gøre valsespalten bredere, modsættes af et modtryk, som tilvejebringes af to hydrauliske cylindre, som trykker mod den 35 løse valses to lejebukke. Dette modtryk indstilles i 2 DK 176712 B1 forvejen ved hjælp af en hydraulisk pumpe til en størrelse, som svarer til den ønskede trykbehandling.Known high pressure roller presses are known for so-called grain bed division of grained goods, such as, for example, cement clinker, which is pressed into the roller slot with extremely high pressure for scaly plates, which are subsequently deagglomerated (brochure "Rollenpresse" No. 11-304 d from KHD Humboldt Wedag AG), whereby the once pressed cargo may exhibit a large proportion of particles already reduced to the desired fineness, for example, 25% may be less than 90 μιη. This high pressure, which in the roller slot acts on the grained goods and which, when displacing the loose roller, would make the roller gap wider, is opposed by a back pressure provided by two hydraulic cylinders which press against the two bearing blocks of the loose roller. This back pressure is pre-set in a hydraulic pump to a size corresponding to the desired pressure treatment.
Hvis dette modtryk overskrides af trykopbygningen inden i valsespalten på grund af det indtrukne kornede gods, 5 så udvider valsespalten sig ved forskydning af den løse valse, indtil der igen indstiller sig en ligevægt mellem det forindstillede modtryk og det af pressegodset frembragte tryk.If this backpressure is exceeded by the pressure build-up within the roll slot due to the retracted grained goods, then the roll gap expands upon displacement of the loose roller until an equilibrium is established between the preset backpressure and the pressure produced.
For at hydraulikvæsken ved en sådan forskydning af 10 den løse valse og dermed også af den hydrauliske cylinder kan strømme væk, er der mellem den hydrauliske cylinder og den hydrauliske pumpe en udligningsbeholder, hvori hydraulikvæske strømmer ind. For herved at undgå et trykfald, er denne udligningsbeholder 15 udformet som boblelager med en gasfyldt boble, som har samme forindstillede tryk, og som bliver sammentrykket på grund af den indstrømmende hydraulikvæske. På denne måde virker boblelageret trykbevarende. Endvidere afdæmpes ved hjælp af den gasfyldte boble i hydraulik-20 systemet forekommende pressetrykspidser, som frembringes på grund af uregelmæssigheder af det kornede gods, hvorved den gasfyldte boble virker som en fjeder.In order for such hydraulic fluid to flow away from such a loose roller and thus also of the hydraulic cylinder, there is a compensating vessel between which the hydraulic cylinder and the hydraulic pump flow into the hydraulic fluid. In order to avoid a pressure drop, this compensating vessel 15 is designed as a bubble bearing with a gas-filled bubble having the same preset pressure and which is compressed due to the flowing hydraulic fluid. In this way, the bubble bearing acts as pressure preservative. Furthermore, pressure pressures which are produced due to irregularities of the grained goods, whereby the gas-filled bubble acts as a spring, are dampened by the gas-filled bubble in the hydraulic system.
Den gasfyldte bobles "fjederkonstant" er fastlagt af størrelsen af det maksimalt anvendelige volumen, som 25 den gasfyldte boble kan udfylde. Ved små boblestørrelser er en lille volumenændring tilstrækkelig til at medføre en forholdsvis stor trykændring, medens trykændringen ved store boblevoluminer forløber mere fladt ved en volumenændring.The "spring constant" of the gas-filled bubble is determined by the size of the maximum usable volume that the gas-filled bubble can fill. For small bubble sizes, a small volume change is sufficient to cause a relatively large pressure change, while the pressure change for large bubble volumes proceeds more flatly with a volume change.
30 Da konstruktionsstørrelsen ved kendte boblelagre i kendte duovalsemaskiner ligger fast, og ændringer af det maksimalt anvendelige gasvolumen kun er mulige ved indbygning af andre boblelagre, er det uden en passende ombygning ikke muligt, ved vekslende driftsbetingelser 35 som følge af ændringer i styrtegodssammensætningen, 3 DK 176712 B1 styrtegodskornstørrelsen, styrtegodstilførselsmængden og lignende, at tilpasse boblelagerfjedervirkningen til disse ændrede driftsbetingelser.30 Since the design size of known bubble bearings in prior art duo rollers is fixed and changes in the maximum usable gas volume are possible only with the incorporation of other bubble bearings, it is not possible without suitable conversion, under varying operating conditions 35 due to changes in the casting composition, 3 DK 176712 B1 Load grain size, Load load amount and the like, to adapt the bubble bearing spring effect to these changed operating conditions.
Opfindelsen har til formål at videreudbygge de 5 kendte hydro-pneumatiske systemer af duovalsemaskiner således, at fjedervirkningen af det hydro-pneumatiske system - også under drift af duovalsemaskinen - på enkel vis kan tilpasses de foreliggende driftsbetingelser uden en tidskrævende og dyr ombygning.The invention aims to further develop the known hydro-pneumatic systems of duo-rolling machines so that the spring action of the hydro-pneumatic system - even during operation of the duo-rolling machine - can be easily adapted to the present operating conditions without a time-consuming and expensive conversion.
10 Dette formål opnås ved hjælp af en indretning ifølge krav l's kendetegnende del og en fremgangsmåde ifølge krav 5's kendetegnende del. Fordelagtige udførelsesformer for opfindelsen er angivet i de afhængige krav.This object is achieved by means of a device according to the characterizing part of claim 1 and a method according to the characterizing part of claim 5. Advantageous embodiments of the invention are set forth in the dependent claims.
15 Ved ifølge opfindelsen at udbygge det hydro-pneu matiske system således, at det maksimalt anvendelige gasvolumen, altså det volumen, som den ifyldte gas maksimalt kan indtage, kan ændres, tilpasses fjedervirkningen af det hydro-pneumatiske system de fore-20 liggende driftsbetingelser på enkel vis uden en tilsvarende ombygning.By expanding the hydro-pneumatic system according to the invention so that the maximum usable gas volume, that is, the volume that the maximum gas can take up to maximum, can be changed, the spring effect of the hydro-pneumatic system can be adapted to the existing operating conditions of simple way without a corresponding conversion.
Hvis der eksempelvis ønskes en stiv fjedervirkning, så opnås dette ved hjælp af en tilsvarende reduktion af det maksimale gasvolumen. Da små oliemæng-25 der, som strømmer ind i udligningsbeholderen og sammentrykker gasboblen, nu bevirker en stor trykstigning inden i gasboblen, er fjedervirkningen tilsvarende stiv. Omvendt frembringer større oliemængder ved en forøgelse af det maksimale gasvolumen kun en lille 30 trykændring inden i gasboblen. Fjedervirkningen er tilsvarende blød.For example, if a rigid spring action is desired, this is achieved by a corresponding reduction in the maximum gas volume. Since small amounts of oil flowing into the equalizing vessel and compressing the gas bubble now cause a large pressure rise within the gas bubble, the spring action is correspondingly rigid. Conversely, by increasing the maximum gas volume, larger amounts of oil produce only a small pressure change within the gas bubble. The spring action is similarly soft.
Ifølge en udførelsesform for opfindelsen opnås ændringen af det maksimale gasvolumen i det hydro-pneumatiske system ved hjælp af en supplerende stempel-35 cylinderenhed, som er fyldt med gas og står i for- 4 DK 176712 B1 bindelse med gasvoluminet i et kendt boblelager. Gasvoluminet i stempelcylinderenheden lader sig på enkel vis ændre trinløst ved forskydning af stemplet ved hjælp af en elektrisk servomotor eller ved hjælp af 5 en mekanisk indstillingsspindel, hvorved det totale gasvolumen - bestående af boblelagerets konstante volumen og stempelcylinderenhedens variable volumen -nu også ændrer sig.According to an embodiment of the invention, the change of the maximum gas volume in the hydro-pneumatic system is achieved by means of a supplementary piston cylinder unit which is filled with gas and communicates with the gas volume in a known bubble storage. The gas volume in the piston cylinder unit can easily be changed infinitely by displacement of the piston by means of an electric servomotor or by means of a mechanical adjusting spindle, whereby the total gas volume - consisting of the constant volume of the bubble bearing and the variable volume of the piston cylinder unit - also changes.
Det mindst mulige gasvolumen, som kan indstilles, 10 svarer så til gasvoluminet af kun boblelageret, og det størst mulige gasvolumen svarer til summen af boblelagerets gasvolumen og stempelcylinderenhedens maksimale gasvolumen.The smallest possible gas volume that can be set then 10 corresponds to the gas volume of the bubble storage only, and the largest possible gas volume corresponds to the sum of the bubble volume gas volume and the maximum gas volume of the piston cylinder unit.
I en yderligere fordelagtig udførelsesform for 15 opfindelsen er boblelageret og stempelcylinderenheden sammenfattet i en integreret konstruktionsdel, hvorved der muliggøres en reduktion af gasvoluminet, hvor reduktionen går ud over boblelagerets gasvolumen, og montage og pladskrav minimeres.In a further advantageous embodiment of the invention, the bubble bearing and piston cylinder assembly are enclosed in an integral structural member, thereby enabling a reduction in the gas volume, the reduction exceeding the bubble volume gas volume, and mounting and space requirements.
20 Yderligere fordele, enkeltheder og træk ved opfindelsen vil blive beskrevet i det følgende ved hjælp af eksempler på udførelsesformer under henvisning til tegningen, på hvilken fig. 1 viser et boblelager med en på gassiden 25 tilsluttet stempelcylinderenhed, og fig. 2 en af et boblelager og en stempelcylinderenhed sammenføjet konstruktionsdel ifølge opfindelsen .Further advantages, details and features of the invention will be described in the following by way of examples of embodiments with reference to the drawing, in which: FIG. 1 shows a bubble bearing with a piston cylinder unit connected to the gas side 25; and FIG. 2 shows a structural part according to the invention joined by a bubble bearing and a piston cylinder unit.
Det hydro-pneumatiske system i udførelsesformen i 30 fig. 1 består af et kendt boblelager 10, der gennem en ledning 18 er forbundet med den hydrauliske cylinder i duovalsemaskinen. Gennem denne ledning 18 strømmer hydraulikvæske 12 ved en udvidelse af valsespalten på grund af stempelbevægelsen af den hydrauliske cylinder 35 ind i boblelageret 10 og sammentrykker den gasfyldte 5 DK 176712 B1 boble 23, som er bevægelig i pilen 19's retning, hvorved gassen 11 i den gasfyldte boble 23 komprimeres yderligere, og trykket i gasboblen 23 stiger. Gassiden af boblelageret 10 er gennem en ledning 13 forbundet 5 med et på tegningen ikke-vist påfyldningsanlæg, eksempelvis en almindelig kommercielt tilgængelig gasflaske, som opfylder boblelagerets gasboble med det ønskede tryk, hvilket kan kontrolleres med et manometer 16 .The hydro-pneumatic system of the embodiment of FIG. 1 consists of a known bubble bearing 10 connected through a conduit 18 to the hydraulic cylinder of the dual roller machine. Through this conduit 18, hydraulic fluid 12 flows through an expansion of the roller slot due to the piston movement of the hydraulic cylinder 35 into the bubble bearing 10 and compresses the gas-filled bubble 23 which is movable in the direction of the arrow 19, whereby the gas 11 in the gas-filled bubble 23 is further compressed and the pressure in the gas bubble 23 increases. The gas side of the bubble bearing 10 is connected through a conduit 13 to a filling system not shown in the drawing, for example, a commercially available gas cylinder which satisfies the bubble of the bubble storage gas at the desired pressure, which can be checked with a pressure gauge 16.
10 Ifølge opfindelsen er denne indretning på gassiden forbundet med en supplerende stempelcylinderenhed 15 således, at det i boblelageret 10 indstillede tryk også er til stede i stempelcylinderenheden 15, uafhængigt af stemplet 22's stilling.10 According to the invention, this device on the gas side is connected to a supplementary piston cylinder unit 15 such that the pressure set in the bubble bearing 10 is also present in the piston cylinder unit 15, irrespective of the position of the piston 22.
15 Stemplet 22's stilling kan ved hjælp af en indret ning 17 ændres trinløst i pilen 21's retning, eksempelvis ved hjælp af en elektrisk servomotor eller ved hjælp af en mekanisk indstillingsspindel. Når stemplet 22 bevæges, ændrer stempelcylinderenhedens gasvolumen 20 11' sig, og på grund af forbindelsen med boblelageret 10's gasvolumen 11 fås således et variabelt indstilleligt totalt gasvolumen, hvis størrelse kan indstilles efter kravene ved drift af duovalsemaskinen.The position of the piston 22 can be changed steplessly in the direction of the arrow 21 by means of a device 17, for example by means of an electric servomotor or by means of a mechanical adjusting spindle. As the piston 22 is moved, the gas volume 20 11 'of the piston cylinder unit changes, and because of the connection with the gas volume 11 of the bubble bearing 10, a variable adjustable total gas volume is obtained, the size of which can be adjusted according to the requirements of operation of the duo roller machine.
Den i fig. 2 viste udførelsesform for opfindelsen 25 forener boblelageret 10 i fig. 1 med den i fig. 1 viste supplerende stempelcylinderenhed ifølge opfindelsen til en integreret konstruktionsdel 20. Her strømmer hydraulikvæsken 12 gennem ledningen 18 ind i konstruktionsdelen 2 0 og trykker mod boblen 23 - som også kan være 30 udformet som et stempel - og som er forskydelig i pilen 19's retning, hvorved gassen 11 komprimeres, og trykket hæves. Gasrummet afgrænses modsat boblen 23 af et bevægeligt stempel 22, hvis stilling ved hjælp af en indretning 17 kan ændres i pilen 21's retning, nø j -35 agtigt som i fig. 1, hvorved størrelsen af det maksi- 6 DK 176712 B1 malt anvendelige gasvolumen, som er afgrænset af stemplet 22 og boblen 23, lader sig ændre trinløst.The FIG. 2, the embodiment of the invention 25 combines the bubble bearing 10 in FIG. 1 with the one shown in FIG. 1 to an integral structural member 20. Here, the hydraulic fluid 12 flows through the conduit 18 into the structural member 20 and presses against the bubble 23 - which may also be formed as a piston - and which is displaceable in the direction of the arrow 19, whereby the gas 11 is compressed and the pressure is raised. The gas compartment is bounded opposite the bubble 23 by a movable piston 22, the position of which can be changed by means of a device 17 in the direction of the arrow 21, exactly like -35 as in FIG. 1, whereby the size of the maximum usable volume of gas delimited by the piston 22 and the bubble 23 is continuously variable.
Ændringen af det maksimalt anvendelige gasvolumen af indretningen i fig. 1 eller indretningen i fig. 2 5 kan gennemføres under drift af duovalsemaskinen, hvorved den under volumenændringen forekommende trykændring inden i gasvoluminet udlignes ved hjælp af opfyldningsindretningen, således at det nødvendige forindstillede driftstryk bevares.The change in the maximum usable gas volume of the device of FIG. 1 or the device of FIG. 2 can be performed during operation of the duo roller machine, whereby the pressure change occurring during the volume change within the gas volume is offset by the filling device so that the necessary preset operating pressure is maintained.
10 Opfindelsen er ikke begrænset til de viste ud førelsesformer, hvor gasvolumenændringerne indstilles ved hjælp af stempelcylinderenheder. Således er også andre foranstaltninger, som fører til ændring af det anvendelige maksimale gasvolumen, fuldt ud i stand til 15 trinløst at ændre fjedervirkningen af det hydro-pneuma-tiske system inden for opfindelsens rammer, eksempelvis ved hjælp af en anden gasboble, som erstatter stemplet 22, og hvis stilling forskydes ved hjælp af et separat hydrauliksystem.The invention is not limited to the embodiments shown, wherein the gas volume changes are adjusted by means of piston cylinder units. Thus, other measures leading to change of the applicable maximum gas volume are also fully capable of continuously changing the spring action of the hydro-pneumatic system within the scope of the invention, for example by means of another gas bubble which replaces the piston 22, and whose position is displaced by a separate hydraulic system.
2020
Claims (6)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19647483 | 1996-11-16 | ||
| DE1996147483 DE19647483B4 (en) | 1996-11-16 | 1996-11-16 | Two-roll machine and method for its operation |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| DK124997A DK124997A (en) | 1998-05-17 |
| DK176712B1 true DK176712B1 (en) | 2009-04-06 |
Family
ID=7811887
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK124997A DK176712B1 (en) | 1996-11-16 | 1997-11-04 | Duo roller machine and method for operating it. |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE19647483B4 (en) |
| DK (1) | DK176712B1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012022871A1 (en) * | 2012-11-22 | 2014-05-22 | Hydac System Gmbh | locking device |
| DE102017002077A1 (en) | 2017-03-04 | 2018-09-06 | Hydrosaar Gmbh | safety device |
| NO344544B1 (en) * | 2018-11-22 | 2020-01-27 | Kongsberg Maritime CM AS | Multi ratio accumulator system. |
| DE102020110468A1 (en) | 2020-04-17 | 2021-10-21 | Khd Humboldt Wedag Gmbh | Method for regulating the damping of the movement of a press roll of a high pressure roller press and corresponding high pressure roller press |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH667500A5 (en) * | 1985-09-26 | 1988-10-14 | Benninger Ag Maschf | Device for controlling the press cylinder to bearing bodies of press roller. |
| DE3705050A1 (en) * | 1987-02-18 | 1988-09-01 | Kloeckner Humboldt Deutz Ag | Two-roller machine, such as a roller press |
| AT398942B (en) * | 1987-04-02 | 1995-02-27 | Laeis & Bucher Gmbh | DOSING DEVICE FOR DETERMINING THE DISCHARGE AND LOAD VOLUME OF THE HYDRAULIC LIQUID OF A DOSABLE ENERGY STORAGE OF A HYDRAULIC SYSTEM, IN PARTICULAR A HYDRAULIC IMPACT PRESS |
| DE4323133A1 (en) * | 1992-07-15 | 1994-01-20 | Luk Lamellen & Kupplungsbau | Expansion tank for hydraulic system of car with electronic clutch management - has cylinder attached to fluid line and spring-loaded piston with ratchet as limiter for fluid chamber |
| DE4226158C2 (en) * | 1992-08-07 | 2003-04-10 | Kloeckner Humboldt Wedag | Process and plant for pressure treatment of granular goods |
-
1996
- 1996-11-16 DE DE1996147483 patent/DE19647483B4/en not_active Expired - Fee Related
-
1997
- 1997-11-04 DK DK124997A patent/DK176712B1/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| DE19647483A1 (en) | 1998-05-20 |
| DK124997A (en) | 1998-05-17 |
| DE19647483B4 (en) | 2007-05-24 |
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