• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A pressure control device for processing machines having at least one roll which has a stationary core around which a hollow roll which forms the roll proper revolves with radial spacing from the core, the hollow roll supported at its ends on the core and supported on the core in between in the radial direction by a fluid pressure medium disposed in a chamber formed at the core, the fluid pressure medium generating a force acting on the inside of the hollow roll to provide the operating pressure of the roll, with a loading device operated by a fluid pressure medium also applied either to the roll or a counter-roll, either the loading device or roll forming a controlling element, with a control pressure which is derived from the pressure prevailing therein used to adjust a pressure in the other controlled element which has a definite predetermined pressure ratio to the pressure in the controlling element, which pressure control device includes a pressure ratio monitoring device having as inputs the control pressure and the actual pressure in the controlled element and compares the inputs and, if the pressure in the controlling element becomes to high relative to a predetermined pressure ratio, reduces the pressure to the controlled element in order to reestablish the desired predetermined pressure ratio.
    公开号:SU999987A3
    申请号:SU772482544
    申请日:1977-05-24
    公开日:1983-02-23
    发明作者:Кюстерс Карл-Хайнц
    申请人:Эдуард Кюстерс (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to control systems for rolling mechanisms and can be used, for example, in paper feed.
    Closest to the invention according to technical essence, 5 is a control system for a rolling mechanism in the form of a hollow roller covering the core> with the formation of two longitudinal closed and isolated liquid chambers along their common axis, and a load roller connected to the load mechanism and interacting with the hollow roll, containing di4> ferennial pressure regulator, connected by 15 hydraulic lines to the fluid chambers of the hollow roll, a pressure transducer connected by control lines to uzochnym mechanism, a pneumatic regulator 20 and the differential pressure, and load control valve device [1].
    A disadvantage of the known device is that in case of malfunctions, for example, in the form of leaks between liquid chambers and a violation, as a result of this, the forces of the interaction of the rolls of the rolling mechanism may cause excessive pressure in the bearings of the rolling mechanism, and this can lead to premature wear of the mechanism.
    The purpose of the invention is to increase the durability of the rolling mechanism.
    This goal is achieved by the fact that the control system is equipped with a pressure regulator in the form of kinematically connected bellows, a throttling valve and a membrane device with working cavities, while each bellows is connected by a hydraulic line to one of the fluid chambers, the throttling valve is controlled by lines with a control device for regulating the load and the membrane device with a control line - with a differential pressure regulator.
    In addition, the control system is equipped with a pneumatic control element, one input of which is connected with pneumatic 999987 4 by a line with the output of the pressure transducer, the other input is connected to the air pump, and the output is connected by a control line to one of the inputs of the pressure regulator. 5
    Finally, a safety valve is installed in the control line connecting the diaphragm device of the pressure regulator to the differential pressure regulator. ; 0
    In FIG. 1. shows a General diagram of the control system of the rolling mechanism; in FIG. 2 - pressure regulator; in FIG. 3 is a diagram of the design of the pressure regulator assembly,. (5 namely its throttle valve, Fig 4 - of embodiment of the pneumatic control circuit;.. Figure 5 - diagram of the differential angle regulator, Fig 6 - a diagram of embodiment 20 of the pressure transmitter..
    The rolling mechanism 1 is made in the form of a hollow roll 2, covering the core 3 with the formation of two longitudinal closed and isolated liquid chambers 4 and 5. along their common axis. These liquid chambers are separated along the generatrix of the hollow roller 2 and core 3 with seals 6. The rolling mechanism 1 also includes a load roller 7, interacting with a hollow roller 2, and a load mechanism 8.
    The rolling mechanism control system 35 includes a differential PE gulyator 9 Pressure connected hydraulic lines 10 and 11 (FIG. 5) from the liquid chambers 4 and 5 respectively, and the pressure transmitter 12 arranged in three corners 13-15. The pressure transducer 12 is connected by control lines 16-19 with a load mechanism 8, as well as with air pumps 20 and 21 and a differential pressure regulator 9. The pneumatic pump 20 4i is connected to the input of each of the nodes 1315. The control system also has a valve device 22 · in the form of klagenov 23-26 (Fig. 1). In addition, the regulator 27 50 Lenia pressures as kinematically interconnected bellows 28 and 29 (Figure 2) includes a control system, the throttle valve 30, the membrane unit 31 with the working cavities 32 and 33. Each of the bellows 28, 55 and 29 connected by a hydraulic line 34 and 35 to the liquid chamber 4 and 5, respectively.
    The throttling valve 30 is connected by control lines 36 and 37 to the valves 23 and 24 of the valve device 22 [load regulation. The membrane device 31 is connected by a control line 38 to a differential pressure regulator 9.
    The control system includes a pneumatic control element 39, the input 40 of which is connected by a pneumatic line 41 to the output 42 of the node 13 of the pressure transducer 12. The second input 43 of the pneumatic control element 39 is connected to the air pump 21, and the output 44 is connected by a control line 36 to the input 45 of the pressure regulator 27. In the control line 38 connecting the membrane device 37 of the pressure regulator 27 to the differential regulator 9, a safety valve 46 is installed. The power supply of the liquid chambers 4 and 5 is carried out by means of a hydraulic line 47 connected on the one hand to the differential regulator 9, and on the other to the pressure source with reservoir 48. The liquid is drained into reservoir 48 from the fluid chamber 5 along line 49 e. To ensure the operation of loading mechanism 8, a hydraulic tank 50 is provided in the system with a pressure source (not indicated), which connected by a hydraulic line 51 to the valves 25 and 26 of the valve device 22 of the load regulation. Each of the valves is connected by hydraulic lines 52 and 53 with hydraulic lines 54 and 55, respectively. The latter are connected to the piston cavities 56 and 57, respectively, of the loading mechanism 8. The other ends of the hydropines 54 and 55 are connected to the source of the fluid supply pressure from the hydraulic tank 50. The pressure regulator 27 has several inputs and outputs: input 58 is connected by pneumatic line 59, with output 60 from node 15 pressure transducer 12, the input 61 is connected to the hydraulic line 34 and further to the liquid chamber 4, the input 62 to the hydraulic line 35 and further to the liquid chamber 5, the input 63 to the control line 37 and the output 64 of the same pressure regulator 27. Valves 23 and 24 are connected by control lines 65 and 66 to valves 25 and 26, respectively. The pressure regulator 27 (Fig. 2) is equipped with a lever 67, which is connected through a roller 68 with a lever 69. The latter is kinematically connected through the rod 70 and the membrane device 31 to the throttling valve 30. The pneumatic control element 39 is similar in design to its throttling valve and membrane device pressure regulator 27 and comprises (Fig. 4) an input 43 connected to a pump 21 and an output 44 connected to a control line 36. Its throttling valve 71 is connected by a rod 72 to a membrane device (not indicated) having working cavities 73 and 74. The differential pressure regulator 9 assembly (Fig. 5) is equipped with a valve 75 that separates the hydraulic lines 10 and 11. The valve 75 is connected by a rod 76 to the piston 77 , which is under the influence of pressure supplied through the control line 38. The node 13 of the pressure transducer 12 has control lines 16 and 17 (lie in the same plane). These lines are connected to two hydraulic power elements (bellows) 78, which are kinematically connected to the levers 79 and 80. The latter is connected via a roller to the lever 81. The lever 81 is connected to the rod 82 and to the valve 83 to convert the input pressure to a certain value. The assembly 14 is similar in design to the assembly 13, and the assembly 15 is similar in construction to the pneumatic control element 39.
    .1 .
    The control system of the rolling mechanism operates as follows.
    During the operation of the rolling mechanism, a certain pressure is set in the load mechanism 8, due to which a certain pressure is placed. And the load roller 7. For the normal operation of the mechanism, it is necessary that from the side of the hollow roll. 2 a certain pressure also acted on the roll 7. The ego is provided due to the pressure difference acting in the liquid chambers 4 and 5. For a greater pressure of the hollow roller 2 to the load roller 7, the pressure in the liquid chamber 4 should be greater than the pressure in the liquid chamber 5. This is achieved due to the fact that the pressure supplied by hydraulic lines 47 and further along the hydraulic lines 10 and 11 into the liquid chambers 4 and 5, respectively, are redistributed (Fig. 5). Pressure redistribution is carried out due to the effect of pressure from the control line 38 on the piston 77 and then on the valve 75. The displacement of the valve 75, for example, to the left (according to the drawing), causes a decrease in the flow of fluid into the fluid chamber 5, from which the fluid is removed via line 49 to the reservoir 48. At the same time, but more liquid enters the fluid chamber 4. This causes the hollow roller 2 to shift toward the load roller 7. In the load mechanism 8 '.
    the pressure is created using a Gypsum tank 50 with a constant pressure source. Further, this pressure is converted to the required value (using the control system) at the inlet to the piston cavities of the cylinders (not indicated) of the load mechanism 8. These pressures are also supplied via control lines 16 and 13 to the nodes 13 and 14 of the pressure transducer 12. The pressure is supplied to these nodes along the control lines 17 and 19 from the rod cavities of the cylinders (not indicated) of the same loading mechanism 8. The working pressure transmitted by the loading roller 7 is the pressure difference between the piston and rod cavities of the loading mechanism 8. If it is necessary to weaken the pressure of the load roll 7 onto the hollow roll 2, then the pressure in the rod cavity of the cylinders of the load mechanism 8 increases. Depending on the pressure developed by the load mechanism 8, .re- 4 the signal from the nodes 13 and 14 30 of the pressure transducer 12 enters the node 15, where, as a fraction of the constant pressure supplied from the air pump 20, is fed to the input 58 of the pressure regulator 27 via the pneumatic line 35 59 and then through the control line 38 to the differential regulator 9 . in the latter occurs such movement of the piston 77 (FIG. 5) and the valve 75, causes the required Ko Thoroe pererasprede4 0 lenye pressure between the fluid chambers 4 and 5 of the hollow roll 2. The pressure in the load mechanism 8 needs to be controlled independently. This is done with the help of a pneumatic pump 21, which supplies constant pressure, which is supplied from a pneumatic pump 21 through a pneumatic control element 31, control lines 36 and 37 to a valve device 22 with valves 23 and m 24. From the latter, an adjustable pressure is supplied via lines 65 and 66 to control valves 25 and 26. in the latter produced by pressure regulation signal conversion, supplied from the fluid container 50 with pressure sources SS com · desired value by Lines 52 and 53 of the hydraulic pressure supplied to idrolinii 54 and 55, and further - a piston cavity cylinders'
    load mechanism 8. The pressure in the latter, as already described, determines the pressure in the control line 38 and, therefore, determines the pressure distribution in the liquid chambers 4 5 to 5.
    If, in the event of a malfunction, for example, of the seal 6 (Fig. 1) in the liquid chamber 4, the required pressure is not reached and excessive leakage of the liquid 10 occurs along line 49, then in the loading mechanism 8 an excess pressure occurs, which will lead to an undesirable load on the rolling machine bearings 1. To exclude 15 of this phenomenon, a pressure regulator 27 is used. The control pressure supplied through the pneumatic line 59 is maintained at the inlet 58, and the pressure in the hydraulic lines 34 and 35 at the inlets 61 and 62, respectively (Fig. 2). The control pressure on the control line 36, being connected to the inlet 45, is throttled in the throttling valve 30 and affects the valves 23 and 24. The last 25 transmit the received signal to the valves 25 and 26, which in turn change the amount of pressure supplied to the loading mechanism 8. The throttling valve 30 does not change the valve bore when the bellows 28 and 29 are in equilibrium, and therefore the membrane device 31 is in equilibrium, into the working half-openings 32 and 33 of which the pressure is supplied from the inlet side 58 and 63 respectively.
    If any element of the system that distorts the control signal supplied by pneumatic line 59 fails, then in this case, to ensure normal control, is the pneumatic control element 39 used (Fig. 4) connected by a pneumatic line 41 to a node 13 in a place where the pressure in the piston cavities of the cylinders of the load mechanism is fixed 8. If this pressure is excessively high, the balance in the position of the rod 72 is disturbed, it displaces under the action of a spring (not indicated) and pressure in the cavity with a spring in the direction of closing the throttle valve 71. This reduces the pressure supplied from the air pump 21 to the control line 36. Following the decrease in pressure in the control line 36, the control pressure in the control line 37 decreases. This reduced pressure causes a corresponding change in pressure in the hydraulic lines 52 and 53 and in the load mechanism 8 so that the pressure developed by it decreases.
    Safety valve 46 is necessary to prevent excessive pressure build-up in control line 38.
    The application of the proposed control system of the rolling mechanism increases the durability of the mechanism.
    权利要求:
    Claims (3)
    [1]
    the output of the pressure transducer is molinpel, the other input is connected to a pneumatic pump, and the output is connected by a control line to one of the inputs of the pressure regulator. Finally, a safety valve is installed in the control line connecting the membrane pressure regulating device with the differential pressure regulator. Fig. 1 shows a general scheme of the control mechanism of the rolling mechanism; in fig. 2 — pressure regulator; in fig. 3 is a schematic design of the pressure regulator assembly,. namely, its throttling valve; in fig. 4 is a schematic diagram of the design of the pneumatic control element; in fig. 5 is a diagram of the angle of the differential controller; in fig. b a design pressure transmitter reference circuit. The milling mechanism 1 is made in the form of a hollow roll 2, covering the hearts 3 with the formation of two longitudinal closed and insulated liquid chambers 4. And 5 along their common axis. These liquid chambers are separated along the seals of the hollow roll 2 and core 3. The milling mechanism 1 also includes a load roller 7, which interacts with a hollow roller 2, and a load mechanism 8. The control system of the milling mechanism includes a differential pressure regulator 9 connected by hydraulic lines 10 and 11 (Fig. 5) with liquid chambers 4 and 5, respectively, as well as a pressure transducer 12, made in the form of three angles 13-15. Pressure transducer 12 is connected by control lines 16-19 to load mechanism 8, as well as to pneumatic pumps 20 and 21 and differential pressure regulator 9. Pneumopump 20 is connected to the input of each of the nodes 1315. The control system also has a valve device 22 in the form of a clapper 23-26 (Fig. 1). In addition, the control system includes a pressure regulator 27 in the form of kinematically interconnected bellows 28 and 29 (Fig. 2 of the throttling valve 30, membrane device 31 with working cavities 32 and 33. Each of the bellows 28 and 29 is connected by hydroline 34 and 35 with a liquid chamber 4 and 5, respectively. The throttling valve ZO lyMM 874 leads 36 and 37 of the control with valves 23 and 24 of the valve device 22 () load control. The membrane device 31 is connected by a control line 38 to a differential pressure regulator 9. The control system includes a pneumatic control element 39, the inlet 40 of which is connected by pneumatic line 41 to the outlet 42 of the assembly 13 of the pressure transducer 12. The second inlet 43 of the pneumatic control element 39 is connected to the pneumatic pump 21, and the outlet 44 is connected by a control line 36 to the inlet 45 of the pressure regulator 27. A control valve 46 is installed in the control line 38 connecting the membrane device 37 of the pressure regulator 27 with the differential regulator 9. The liquid chambers 4 and 5 are powered by a hydraulic line 47 connected on one side to the differential regulator 9, and from another to the pressure source with the reservoir 48. The liquid is drained into the reservoir 48 from the liquid chamber 5 via line 49, ensuring the operation of the loading mechanism 8 in the system is provided with a hydraulic tank 50 with a pressure source (not labeled) oedinen hydraulic line 51 with the valves 25 and 26, valve assembly 22 controlling load. Each of the valves is connected by hydraulic lines 52 and 53 to hydraulic lines 54 and 55, respectively. The latter are connected to the piston cavities 56 and 57, respectively, of the load mechanism 8. The other ends of the hydrolines 54 and 55 are connected to the pressure supply source of the fluid from the hydraulic tank 50. The pressure regulator 27 has several inlets and outlets: the inlet 58 is connected by pneumatic lip 59, to the outlet 6O from node 15 of pressure transducer 12, input 61 is connected to hydroline 34 and further to liquid chamber 4, input 62 to hydraulic line 35 and further to liquid chamber 5, input 63 to control line 37 and output 64 of the same pressure regulator 27 . Valves 23 and 24 are connected by control lines 65 and 66 to valves 25 and 26, respectively. The pressure regulator 27 (Fig. 2) is provided with a lever 67, which is connected via roller 68 to lever 69. The latter is connected kinematically through the rod 70 and the membrane device 31 to the throttling valve AOR. The pneumatic control element 39, by the design of its throttling valve and the membrane device, is similar to a pressure regulator, 27, and contains (FIG. 4) an inlet 43, connected to a pump 21, and an outlet 44, connected to a control line 36. Its throttling valve 71 is connected by a stem 72 to a membrane device (not indicated) having working cavities 73 and 74. The differential pressure regulator assembly 9 (Fig. 5) is equipped with a valve 75 separating the hydraulic lines 10 and 11. The valve 75 is connected by a rod 76 to a piston 77, which is influenced by pressure applied through control line 38. Node 13 of pressure transducer 1 has control lines 16 and 17 (lies in one plane). These lines are connected to two hydraulic power elements (bellows) 78, which are kinematically connected with. chagas 79 and 80. The latter is connected via a roller to the lever 81. The lever 81 is connected to the rod 82 and to the valve 83 to convert the applied pressure to a certain value. The assembly 14 is similar in construction to assembly 13, and the assembly 15 is similar in construction to the pneumatic control element 39. The control system of the rolling mechanism works in the following way. During the operation of the rolling mechanism, a certain pressure is established in the load mechanicsim 8, due to which there is a certain pressure under pressure. And the load roller 7. For normal operation of the mechanism it is necessary that the roller 7 also has a certain pressure acting from the side of the hollow roll 2. This is ensured by the pressure difference acting in the fluid chambers 4 and 5. In order to press the hollow roll 2 more against the load roll 7, the pressure in the liquid chamber 4 must be greater than the pressure in the liquid chamber 5. This is due to the fact that the pressure applied along line 47 and further along line 10 and 11 into liquid chambers 4 and 5, respectively, redistributed (Fig. 5). The redistribution of pressures is due to the pressure from the control line 38 on the pores of the 77 and then on the valve 75. Offset of the valve 75, for example, to the left (according to the drawing), causes a decrease in the flow of liquid into the liquid chamber 5, the short-circuit of which the liquid is removed 49 into the reservoir 48. Simultaneously, more liquid enters the liquid chamber 4. This causes the hollow roll 2 to move towards the loading roll 7. In the loading mechanism 8 .., pressure is created with hydraulic tank 50 with a constant pressure source. Further, this pressure is converted to the required value (by means of a control system) at the entrance to the piston cavities of the cylinders (not indicated) of the load mechanism 8. These pressures are also supplied via lines 16 and 13 of the recovery unit to the nodes 13 and 14 of the pressure converter 12. The same pressure is supplied to the same nodes along control lines 17 and 19 from cylinder rod cavities (not indicated) of the same loading mechanism 8. The working pressure transmitted by the load roller 7 is the pressure difference between the piston and rod cylinder of the loading mechanism 8. If it is necessary to relieve the pressure of the loading roller 7 on the hollow roller 2, the pressure in the rod cavity of the cylinders of the loading mechanism 8 rises. Depending on the pressure developed by the loading mechanism 8, the resultant The signal from nodes 13 and 14 of pressure transducer 12 goes to node 15, from which, as a fraction of the constant pressure supplied from the pneumopump 2O, is fed to the input 58 of the pressure regulator 27 via the pneumatic line 59 and further along the control line 38 to the differential regulator 9 In the latter, there is such a movement of the piston 77 (Fig. 5) and the valve 75, which causes the required redistribution of pressure between the liquid chambers 4 and 5 of the hollow roll 2. The pressure in the load mechanism 8 must be independently controlled. This is done by means of a Pneumopump 21, which supplies a constant pressure, which from the pneumopump 21 through the pneumatic control element 31, the control lines 36 and 37 is supplied to the valve device 22 with valves 23 and 24. From the latter, the regulated pressure value is fed through lines 65 and 66 controls to valves 25 and 26. In the latter, according to the control signal, the pressure supplied from the hydraulic tank 5 with a pressure source is converted. The required hydraulic pressure across hydrolines 52 and 53 enters the hydrolines 54 and 55 and then into the 1st cavity of the cylinder of the loading mechanism 8, the pressure in the latter way determines the pressure in the control line 38 and, therefore, determines the pressure distribution in liquid chambers 4 and 5. If, in the event of a malfunction, for example, seal 6 (Fig. 1), the required pressure is not reached in the liquid chamber 4 and an excessive leakage of fluid occurs through the pipeline. 49, an overpressure occurs in the load mechanism 8, which will lead to an undesirable load on the bearings of the rolling mechanism 1. A pressure regulator 27 is used to eliminate this phenomenon. The control pressure supplied by the pneumatic line 59 is maintained at the inlet 58, and the pressure in the hydraulic lines 34 and 35 at the inlets 61 and 62, respectively (Fig. 2). The control pressure on control line 36, being connected to the inlet 45, is throttled in the throttling valve AOR and affects the valves 23 and 24. P1 the latter transmit the received signal to valves 25 and 26, and those in turn change the amount of pressure applied to load mechanism 8. The throttling valve 30 does not change the valve section when the bellows 2 and 29 are in equilibrium, therefore, the membrane device 31 is in equilibrium, to which 32 and 33 are supplied with pressure from the inputs 5 8 and 63 respectively. If any element of the system that distorts the control signal supplied by the pneumatic line 59 fails, then the pneumatic control element 39 (Fig. 4) j is connected to the node 13 at the place where the pressure is fixed to ensure normal control. in the piston cavities of the load mechanism 8. If this pressure is excessively high, the equilibrium in the position of the rod 72 is disturbed, it is displaced under the action of a spring (not indicated) and the pressure in the cavity with a spring in Close the throttling valve 71. Due to this, the pressure supplied from the pneumatic pump 21 to the control line 36 is reduced. Following a decrease in pressure in control line 36, control pressure in control control 37 is reduced. This reduced pressure causes a corresponding pressure in the hydrolines 52 and 53 and in the load mechanism 8 in such a way that the pressure developed by it decreases. A safety clutch 46 is required to avoid excessive pressure build-up on control line 38. Prilling of the proposed control system by a rolling mechanism increases the durability of the mechanism. Claim 1. The control system of the rolling mechanism in the form of a hollow roll, covering the core with the formation along their common axis of two longitudinal closed and isolated between each other liquid chambers, and the load Bajv: Esa, connected to the load mechanism and interacting with a hollow roll, containing a differential pressure control, connected by hydrolines to hollow-roll liquid chambers,: pressure forming agent, connected by 1 control lines to the load mechanism, pneumatic pumps and differential A potential pressure regulator and a valve load control device, characterized in that, in order to increase the durability of the rolling mechanism, it is equipped with a pressure regulator in the form of kinematically interconnected bellows, a throttling valve and a membrane device with working cavities, each bellows is connected by a hydraulic line with one of the liquid chambers, the throttling valve of the control lines is connected to a valve-controlled load control device, and the membrane device is controlled by a control line with a ziff entsialnym toromdavleni regulator.
    [2]
    2. A system according to claim 1, characterized in that it is provided with a stump & control element, one input of which is connected to the output of the pressure transducer, the other input is connected to the pneumatic pump, and the output is connected to one of the pressure regulator's inputs.
    [3]
    3. The system according to claim 1, (i tl and h ayu with 51 in that a relief valve is installed in the control line connecting the membrane device of the pressure regulator with the differential pressure regulator. The sources of information received into account during the examination 1. German Patent No. 1411327, class 55e, 1/05, published 1973.
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    同族专利:
    公开号 | 公开日
    SE7704900L|1977-11-27|
    BR7703332A|1978-11-28|
    DE2623492A1|1977-12-08|
    US4154160A|1979-05-15|
    FI61219B|1982-02-26|
    FI61219C|1982-06-10|
    FI771396A|1977-11-27|
    CA1065700A|1979-11-06|
    JPS52144561A|1977-12-01|
    SE428047B|1983-05-30|
    GB1573383A|1980-08-20|
    DE2623492B2|1980-10-02|
    CH620777A5|1980-12-15|
    JPS6154963B2|1986-11-26|
    DE2623492C3|1981-06-04|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    US2908964A|1957-01-18|1959-10-20|Kuesters Eduard|Pressure treatment of material|
    FR1209588A|1958-07-04|1960-03-02|Cylinder arrangement for compression processing of strip material|
    US3119324A|1960-08-29|1964-01-28|Beloit Iron Works|Controlled deflection roll|
    JPS4323043Y1|1968-05-09|1968-09-30|
    DE2305685B2|1973-02-06|1975-02-13|Maschinenfabrik Koeppern & Co Kg, 4320 Hattingen|Hydraulic support for the slidingly mounted roller in roller presses|
    CH589806A5|1975-03-04|1977-07-15|Escher Wyss Ag|CH627243A5|1978-03-01|1981-12-31|Escher Wyss Ag|
    DE2825706A1|1978-05-22|1979-11-29|Escher Wyss Ag|DEVICE FOR DETERMINING THE PRESSURE FORCE ACTING IN A ROLLING DEVICE WITH AT LEAST ONE DEFLECTION ADJUSTING ROLLER AND AT LEAST ONE COUNTER ROLLER|
    DE2849253C2|1978-11-08|1981-01-08|Escher Wyss Ag, Zuerich |Deflection adjustment roller|
    AT373310B|1980-02-05|1984-01-10|Escher Wyss Ag|DEFLECTION ADJUSTING ROLLER FOR PRESSURE TREATMENT OF MATERIAL SHEETS, IN PARTICULAR PAPER SHEETS|
    DE3024570C2|1980-06-28|1987-12-17|Kuesters, Eduard, 4150 Krefeld, De|
    DE3109536C2|1981-03-13|1994-04-14|Sulzer-Escher Wyss Ag, Zuerich, Ch|
    US4406139A|1981-06-06|1983-09-27|H. Krantz Gmbh & Co.|Roller arrangement for dewatering fabrics|
    US4527473A|1981-07-13|1985-07-09|Littleton Francis J|Thermal adjustment apparatus for rotating machines|
    FI72551C|1983-09-16|1987-06-08|Waertsilae Oy Ab|Control device for roller press.|
    DE3516535C2|1985-05-08|1988-12-08|Kleinewefers Gmbh|
    DE3622398C1|1986-02-18|1987-06-19|Escher Wyss Ag|Sepg. calender rolls - involves lowering pressure in hydraulic carrier support installations with time delay w.r.t. pressure to prevent damage to roll surface|
    DE3815002A1|1988-05-03|1989-11-16|Krupp Polysius Ag|GOOD BED ROLL MILL|
    DE8817076U1|1988-12-08|1992-11-05|Eduard Kuesters Maschinenfabrik Gmbh & Co Kg, 4150 Krefeld, De|
    US5244448A|1989-05-22|1993-09-14|Valmet Paper Machinery Inc.|Method and apparatus for regulating the temperature of an adjustable-crown roll|
    US6644332B1|2001-01-25|2003-11-11|Fisher Controls International Inc.|Method and apparatus for multiple-input-multiple-output control of a valve/actuator plant|
    EP2711666A1|2012-09-20|2014-03-26|Boegli-Gravures S.A.|Method for manufacturing a set of embossing rollers that cooperate with one another and model device to execute the method|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE2623492A|DE2623492C3|1976-05-26|1976-05-26|Pressure control device for rolling equipment|
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