EP3380257B1 - Régulateur de débit volumique - Google Patents

Régulateur de débit volumique Download PDF

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Publication number
EP3380257B1
EP3380257B1 EP16787882.6A EP16787882A EP3380257B1 EP 3380257 B1 EP3380257 B1 EP 3380257B1 EP 16787882 A EP16787882 A EP 16787882A EP 3380257 B1 EP3380257 B1 EP 3380257B1
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EP
European Patent Office
Prior art keywords
volume flow
channel
pressure chamber
piston
regulating valve
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
Application number
EP16787882.6A
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German (de)
English (en)
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EP3380257A1 (fr
Inventor
Daniel Knie
Johannes Alken
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SMS Group GmbH
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SMS Group GmbH
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Publication date
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Publication of EP3380257A1 publication Critical patent/EP3380257A1/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/07—Adaptation of roll neck bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/07—Adaptation of roll neck bearings
    • B21B31/074—Oil film bearings, e.g. "Morgoil" bearings
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors

Definitions

  • the invention relates to a volume flow control valve for controlling the volume flow of a fluid medium in two outlet channels.
  • the invention relates to the use of such a volume flow control valve in a chock for rotatably supporting a roll neck of a roll in a roll stand for rolling preferably metallic rolling stock.
  • Volume flow control valves are fundamentally known in the prior art. B. from the EP 1 452 381 A1 , the EP 1 653 132 B1 , the GB 815 622 A or the DE 2051 949 A1 .
  • German patent application DE 2051 949 A1 discloses a volume flow control valve according to the preamble of claim 1.
  • this document discloses a volume flow control valve with a cylinder, in the cavity of which a dumbbell-shaped double piston is axially displaceably guided.
  • the double piston consists of a first and a second piston, which are connected to each other via a tapered center piece.
  • a central pressure chamber of the volume flow control valve is formed in the area of the tapered center piece.
  • Springs are arranged on the end faces of the cylinder, which extend into the interior of its cavity and between which the double piston is held in a central position.
  • a first and a second peripheral pressure chamber of the volume flow control valve are formed in the area of the springs.
  • An inlet channel and a first outlet channel are provided in the cylinder for inlet and outlet of a fluid medium into the cylinder.
  • chocks as oil film bearings for roll journals of a roll in a roll stand for rolling metallic rolling stock is known in the prior art.
  • the chock disclosed there comprises a bearing bush which spans a cylindrical receiving space for the roll neck.
  • the bearing bush On its inside, the bearing bush has, for example, two hydrostatic pockets, which are arranged essentially in a common axial line and can be fed with a coolant and / or lubricant via a check valve and through bores running in the bearing bush or the installation piece. Throttles in the bores should ensure optimal hydrostatic support of the roll neck even when the roll neck is inclined in the bearing bush.
  • the chokes also called restrictors or orifices, perform precisely this function, but in practice only unsatisfactorily.
  • the throttles or restrictors are not suitable for distributing the volume flow of fluid medium or coolant and / or lubricant evenly over the two hydrostatic pockets, in particular not when the roll neck is inclined in the receiving space.
  • the throttles or restrictors show high pressure losses, sometimes over 200 bar.
  • German published application 2751082 discloses a volume flow control valve according to the preamble of claim 1.
  • the invention is based on the object of developing a known volume flow control valve, in particular for use in connection with an installation piece for storing roller journals, in such a way that the volume flow of the fluid medium in the outlet channels of the volume flow control valve also with different pressure ratios in the outlet channels is evened out.
  • middle position also means symmetry position.
  • the opening cross-sectional areas released by the two outlet channels are greater than zero; ie in this
  • the fluid medium can flow away from the center or symmetry position; in any case, the drainage channels are not blocked.
  • This claimed design of the volume flow control valve is the constructive prerequisite for solving the above-mentioned task, namely ensuring that the volume flows in the first outlet channel and in the second outlet channel can each be kept the same, even with different pressure conditions in the outlet channels.
  • the length L of the center piece of the double piston is, for example, equal to the distance 2d between the center axes of the first and the second outlet channel.
  • the first and second pistons of the double piston are cylinders, the end faces of which, also called control edges for the outlet channels, extend perpendicular to the center piece, this claimed length of the center piece ensures that - if the double piston is in the middle position - the first outlet channel through the first piston of the double piston and the second outlet channel through the second piston of the double piston are each only half closed.
  • the double piston also called valve spool
  • the double piston also called valve spool
  • a first pressure channel is provided for supplying the static pressure in the first discharge channel to the second peripheral pressure chamber and that a second pressure channel is provided for supplying the static pressure in the second discharge channel to the first peripheral pressure chamber.
  • a first plunger is axially displaceably mounted in the first peripheral pressure chamber to act on the end face of the first piston of the double piston delimiting the first peripheral pressure chamber, the first plunger being able to act upon the total pressure in the first outlet channel is and that in the second peripheral pressure chamber, a second plunger is axially displaceably mounted to act on the end face of the second piston of the double piston delimiting the second peripheral pressure chamber, wherein the second plunger can be acted upon by the total pressure in the second outlet channel.
  • the double piston automatically adjusts itself according to a balance of forces which results from the pressure conditions and preferably also the spring forces in the two peripheral pressure chambers.
  • the double piston By acting on the peripheral pressure chambers with the pressures mentioned, the double piston is automatically positioned in relation to the outlet channels in such a way that the desired volume flow of the same amount is set in the outlet channels.
  • volume flow control valve For the intended use of the volume flow control valve described in the following for chocks for storing support rolls in roll stands, it is advantageous if the volume flow control valve is designed for pressures of up to 2,000 bar.
  • the chock is characterized in that a volume flow control valve according to the invention is provided for controlling the volume flow of the coolant and / or lubricant as a fluid medium in the receiving space of the chock.
  • the first drain channel of the volume flow control valve is then connected to the first feed channel and the second drain channel is connected to the second feed channel for feeding the coolant and / or lubricant into the receiving space of the chock.
  • This claimed and inventive design of the chock advantageously ensures that even when the roll neck is inclined in the receiving space of the chock, the volume flows of the cooling and / or Lubricant in the two feed channels to the receiving space are always the same size.
  • volume flow control valve and the chock are the subject of the dependent claims.
  • Figure 1 shows the volume flow control valve 100 according to the invention. It essentially consists of a cylinder 110, in which a dumbbell-shaped double piston 120 is axially displaceably mounted.
  • the term "axial" is used in the sense of the invention for the direction of movement of the double piston.
  • the double piston 120 consists of a first piston 120-1 and a second piston 120-2, which are firmly connected to one another via a tapered central piece 126.
  • the first and second pistons lie as tightly as possible against the cylinder wall.
  • a central pressure chamber 130 of the volume flow control valve 100 is formed in the region of the tapered center piece 126.
  • a first peripheral pressure chamber 150-1 and a second peripheral pressure chamber 150-2 are formed in the end regions of the cylinder, each of which is bounded by the end faces of the first and second pistons facing away from the center piece 126.
  • an inlet channel 160 is formed for supplying a fluid medium, for example a coolant and / or lubricant, with the aid of a pump device 250 into the central pressure chamber 130.
  • a central outlet chamber 170-1 and a second outlet channel 170-2 are formed in the central pressure chamber 130.
  • the first and the second outlet channels 170-1, 170-2 each have the same axial distance d on both sides of the inlet channel 160.
  • the length L of the central piece 126 of the double piston 120 preferably corresponds to the distance 2d of the central axes of the first and the second Drain channel 170-1, 170-2. This ensures that - when the double piston 120 is in a central position - the first outlet channel 170-1 is closed by the first piston 120-1 and that at the same time the second outlet channel 170-2 is closed by the second piston 120-2 are that both share the same opening cross-sectional area.
  • a spring 140 is preferably arranged in each of the peripheral pressure chambers 150-1, 150-2 in order to hold the double piston in a central position, in particular when the volume flow control valve is not in operation. However, the springs 140 do not prevent the basic possibility of axially displacing the double piston 120 within the cylinder 110.
  • the above-mentioned object of the invention namely to ensure the same volume flows in the first and second discharge channels 170-1, 170-2 even with different pressure conditions there, is achieved in particular by the peripheral pressure chambers 150-1, 150-2 of the Volume flow control valve are suitably pressurized with certain pressures.
  • the first peripheral pressure chamber 150-1 is subjected to the static pressure in the second drain line 170-2 for this purpose.
  • the second peripheral pressure chamber 150-2 is subjected to the static pressure in the first outlet channel 170-1.
  • the application takes place via a respectively provided first and second pressure channel 180-1, 180-2.
  • a first plunger 190-1 is axially displaceably mounted in the first peripheral pressure chamber 150-1 for acting on the end face of the first piston 120-1 of the double piston delimiting the first peripheral pressure chamber.
  • the first plunger 190-1 is acted upon by the total pressure in the first outlet channel 170-1 via a pressure channel.
  • a second plunger 190-2 is axially displaceably mounted in the second peripheral pressure chamber 150-2 for acting on the second peripheral pressure chamber 150-2 delimiting end face of the second piston 120-2 of the double piston.
  • the second plunger 190-2 is pressurized with the total pressure in the second outlet channel 170-2 via a pressure channel.
  • the pressure channels are in Figure 1 shown as dashed lines.
  • Figure 2 shows the connection of the pressure channels for the static and the total pressure to the first or the second discharge channel 170-1, 170-2.
  • a fluid medium flows in the discharge channels 170-1, 170-2.
  • This can be a coolant and / or lubricant, which from the central pressure chamber 130 to a consumer, e.g. B. flows a chock for rotatably supporting a roll neck.
  • the fluid medium within the drainage channels shows a speed distribution as shown in Figure 2 is shown with reference number 1.
  • a pitot probe which is oriented in such a way that the fluid medium flows into the pitot probe, is provided to record the total pressure p total in the discharge channel.
  • an opening is provided on the wall of the drain channel 170, which represents the end of the first or second pressure channel 180-1, 180-2 for detecting the static pressure p Stat in the drain channel.
  • the double piston 120 adjusts itself automatically or automatically in accordance with a balance of the forces acting on it.
  • This equilibrium of forces is established in particular on the basis of the forces acting on the end faces of the first and second pistons 120-1, 120-2 facing away from the center piece 126.
  • the forces are, on the one hand, the force which results from the action of the static pressures on the end faces of the first and the second piston and the force which is exerted by the tappets on the same end faces.
  • the force exerted by the springs 140 on the same end faces also influences the balance of forces.
  • the balance of forces determines the axial position of the double cylinder and thus also the ratio of the degree of opening of the first outlet channel to the degree of opening of the second drain channel. In accordance with this ratio of the degrees of opening, the volume flows in the first and the second outlet channels 170-1, 170-2 can be set to the same amount.
  • FIG 3 shows the said application of the volume flow control valve 100 according to the invention in connection with a chock 200.
  • the chock 200 is used for rotatably supporting a roll neck 300 of a roll in a roll stand for rolling rolling stock.
  • the chock 200 has a cylindrical receiving space 210, in which the roll neck 300 is rotatably mounted.
  • the cylindrical receiving space is typically spanned by a bearing bush 220, which is inserted into the chock 200 as a wearing part.
  • On the inner wall of the bearing bush 220 On the inner wall of the bearing bush 220, a plurality, typically 2 hydrostatic pockets 2, 3 are formed, through which the coolant and / or lubricant is pumped under high pressure into the receiving space 210, more precisely into the annular gap between the bearing bush 220 and the roll neck 300 becomes.
  • the first outlet channel 170-1 of the volume flow control valve also called the first feed channel
  • the second outlet channel 170-2 of the volume flow control valve also called the second feed channel, with the second hydrostatic
  • volume flow control valve 100 in connection with the chock 200, it is advantageous if the volume flow control valve is designed for pressures up to 2,000 bar.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Safety Valves (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Multiple-Way Valves (AREA)

Claims (7)

  1. Soupape de réglage (100) pour le débit volumique, présentant :
    un cylindre (110) comprenant un double piston (120) en forme d'haltère guidé dans l'espace creux du cylindre en question, double piston qui présente un premier piston (120-1) et un second piston (120-2) qui sont reliés à demeure l'un à l'autre par l'intermédiaire d'un élément central (126) de forme conique ; dans lequel, dans la zone de l'élément central de forme conique, on réalise une chambre de pression centrale (130) de la soupape de réglage pour le débit volumique ;
    une première et une deuxième chambre de pression périphérique (150-1, 150-2) dans le cylindre de la soupape de réglage pour le débit volumique, qui sont délimitées par les côtés frontaux du premier et du second piston, qui se détournent de l'élément central (126) ; et
    dans le cylindre, un canal d'alimentation (160) et un premier canal d'évacuation (170-1) pour l'alimentation, respectivement l'évacuation d'un milieu fluide dans la chambre de pression centrale (130), respectivement à partir de cette dernière ;
    dans lequel, à côté du premier canal d'évacuation (170-1), on prévoit un second canal d'évacuation (170-2) pour l'évacuation du milieu fluide à partir de la chambre de pression centrale (130) ; et
    dans lequel le premier et le second canal d'évacuation (170-1, 170-2) sont disposés contre le cylindre, à une distance axiale 2d telle que - lorsque le double piston (120) se trouve dans une position médiane par rapport aux deux canaux d'évacuation - le premier canal d'évacuation (170-1) - de préférence dans un état dans lequel il est recouvert en partie par le premier piston (120-1) - et le second canal d'évacuation (170-2) - de préférence dans un état dans lequel il est recouvert en partie par le second piston (120-2) - libèrent respectivement une surface de section transversale d'ouverture identique ;
    caractérisée
    ce que l'on prévoit un premier canal de pression (180-1) pour l'acheminement de la pression statique régnant dans le premier canal d'évacuation (170-1) jusque dans la deuxième chambre de pression périphérique (150-2) ;
    en ce que l'on prévoit un second canal de pression (180-2) pour l'acheminement de la pression statique régnant dans le second canal d'évacuation (170-2) jusque dans la première chambre de pression périphérique (150-1) ;
    en ce que, dans la première chambre de pression périphérique (150-1), est monté un premier coulisseau (190-1) apte à se déplacer en direction axiale, destiné à agir sur le côté avant du premier piston (120-1) du double piston, qui délimite la première chambre de pression périphérique; dans lequel le premier coulisseau (190-1) peut être sollicité avec la pression totale régnant dans le premier canal d'évacuation (170-1) ; et
    en ce que, dans la deuxième chambre de pression périphérique (150-2), est monté un second coulisseau (190-2) apte à se déplacer en direction axiale, destiné à agir sur le côté avant du second piston (120-2) du double piston, qui délimite la deuxième chambre de pression périphérique; dans lequel le second coulisseau (190-2) peut être sollicité avec la pression totale régnant dans le second canal d'évacuation (170-2).
  2. Soupape de réglage (100) pour le débit volumique selon la revendication 1,
    caractérisée
    en ce que la soupape de réglage pour le débit volumique est dimensionnée pour des pressions s'élevant jusqu'à 2000 bar.
  3. Soupape de réglage (100) pour le débit volumique selon l'une quelconque des revendications précédentes,
    caractérisée
    en ce que, dans la première et dans la seconde chambre de pression périphérique (150-1, 150-2), est disposé respectivement un ressort (140), ressorts entre lesquels est maintenu le double piston - tout en étant à même de pouvoir se déplacer en direction axiale - dans la position médiane.
  4. Empoise (200) pour le montage en rotation d'un tourillon de cylindre (300) d'un cylindre dans une cage de laminoir destinée au laminage d'un produit à laminer :
    comprenant un espace de réception cylindrique (210) destiné à la réception du tourillon de cylindre (300) ;
    comprenant un premier et un second canal d'alimentation (170-1, 170-2) pour acheminer des moyens de refroidissement et/ou de lubrification dans l'espace de réception (210) ; et
    comprenant un élément qui est destiné au réglage du débit volumique du moyen de refroidissement et/ou de lubrification dans les canaux d'alimentation (170-1, 170-2) ;
    caractérisée
    en ce que l'élément est réalisé sous la forme d'une soupape de réglage (100) pour le débit volumique selon l'une quelconque des revendications précédentes ;
    en ce que le milieu fluide est réalisé sous la forme d'un moyen de refroidissement et/ou de lubrification ; et
    en ce que le premier canal d'évacuation (170-1) de la soupape de réglage (100) pour le débit volumique est raccordé au premier canal d'alimentation de l'empoise et le second canal d'évacuation (170-2) est raccordé au second canal d'alimentation de l'empoise.
  5. Empoise selon la revendication 4,
    caractérisée
    en ce qu'au moins un des canaux d'alimentation débouche dans une poche hydrostatique (2, 3) qui est réalisée contre la paroi interne de l'espace de réception.
  6. Empoise selon la revendication 5,
    caractérisée
    en ce que l'espace de réception (210) est maintenu à l'état tendu par l'intermédiaire d'une douille de palier (220) qui est incorporée dans l'empoise (200) pour faire office d'élément d'usure ; et
    en ce que la poche hydrostatique (2, 3) est réalisée contre le côté interne de la douille de palier (220).
  7. Empoise selon l'une quelconque des revendications 4 à 6,
    caractérisée
    en ce qu'on prévoit un mécanisme de pompage (250) destiné à l'acheminement du moyen de refroidissement et/ou de lubrification, de préférence avec des pressions allant jusqu'à 2000 bars, via le canal d'alimentation (160), jusque dans la chambre de pression centrale (130) de la soupape de réglage (100) pour le débit volumique.
EP16787882.6A 2015-11-23 2016-10-28 Régulateur de débit volumique Active EP3380257B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015223013.9A DE102015223013A1 (de) 2015-11-23 2015-11-23 Volumenstrom-Regelventil
PCT/EP2016/076029 WO2017089067A1 (fr) 2015-11-23 2016-10-28 Régulateur de débit volumique

Publications (2)

Publication Number Publication Date
EP3380257A1 EP3380257A1 (fr) 2018-10-03
EP3380257B1 true EP3380257B1 (fr) 2020-03-18

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EP16787882.6A Active EP3380257B1 (fr) 2015-11-23 2016-10-28 Régulateur de débit volumique

Country Status (8)

Country Link
US (1) US10974296B2 (fr)
EP (1) EP3380257B1 (fr)
JP (1) JP6586526B2 (fr)
CN (1) CN108290189B (fr)
DE (1) DE102015223013A1 (fr)
RU (1) RU2691004C1 (fr)
TW (1) TWI616606B (fr)
WO (1) WO2017089067A1 (fr)

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CN108908880B (zh) * 2018-06-28 2020-06-30 滁州质顶机电科技有限公司 一种家用电器外壳用注塑模具
BE1027205A9 (fr) * 2019-04-17 2020-11-23 Safran Aero Boosters Sa Vanne fluidique passive de répartition de débits fixes
CN110274043A (zh) * 2019-07-19 2019-09-24 优刻得科技股份有限公司 流量平衡装置

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Publication number Publication date
WO2017089067A1 (fr) 2017-06-01
JP6586526B2 (ja) 2019-10-02
CN108290189A (zh) 2018-07-17
US10974296B2 (en) 2021-04-13
DE102015223013A1 (de) 2017-05-24
TW201723368A (zh) 2017-07-01
RU2691004C1 (ru) 2019-06-07
US20180345340A1 (en) 2018-12-06
CN108290189B (zh) 2019-08-27
TWI616606B (zh) 2018-03-01
EP3380257A1 (fr) 2018-10-03
JP2018536127A (ja) 2018-12-06

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