EP2325500A1 - Commande pivotante - Google Patents

Commande pivotante Download PDF

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Publication number
EP2325500A1
EP2325500A1 EP09014559A EP09014559A EP2325500A1 EP 2325500 A1 EP2325500 A1 EP 2325500A1 EP 09014559 A EP09014559 A EP 09014559A EP 09014559 A EP09014559 A EP 09014559A EP 2325500 A1 EP2325500 A1 EP 2325500A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
drive
drive housing
pressure medium
piston
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.)
Withdrawn
Application number
EP09014559A
Other languages
German (de)
English (en)
Inventor
Harald Wagner
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.)
Mig GmbH
Original Assignee
Mig 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 Mig GmbH filed Critical Mig GmbH
Priority to EP09014559A priority Critical patent/EP2325500A1/fr
Priority to DE202010012575U priority patent/DE202010012575U1/de
Publication of EP2325500A1 publication Critical patent/EP2325500A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
    • F15B15/065—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement the motor being of the rack-and-pinion type

Definitions

  • the invention relates to a pivot drive according to the features 1.1 to 1.10 of claim 1 and the features 2.1 to 2.10 of claim 2.
  • Rotary actuators of the aforementioned type are used in particular for actuating shut-off devices, e.g. Valves, throttle valves or the like used mainly in petrochemical or chemical plants.
  • the pivot drives known in the prior art have a drive housing in which an outgoing drive shaft is pivotally mounted.
  • the drive housing extends transversely to the shaft axis of the drive shaft tubular and forms there usually two coaxial cylinders, which are provided at their free ends with cylinder covers.
  • the cylinder cover are connected by screws with the wall of the associated cylinder and optionally have centrally located stroke limiter in the form of protruding into the cylinder inside screws, which can be adjusted by screwing or unscrewing.
  • pistons are displaceably guided, on whose opposite inner sides in each case a rack is mounted, which surround the drive shaft on both sides and there mesh with a rotatably mounted on the drive shaft pinion. Because of this kinematic Connection, the pistons in the cylinders can only move in opposite directions. Their translational movement is converted into a rotational movement of the drive shaft.
  • the rotary actuator can be single-acting or double-acting.
  • the pistons limit pressure chambers either only on their insides or only on their outsides.
  • the pressure chambers are connected via feed channels in the housing with an externally accessible pressure medium connection. About this they can be acted upon with a pressure medium, usually compressed air.
  • a pressure medium usually compressed air.
  • the pistons are displaced outwards when pressurized and reversed in the case of external pressure chambers. So that the pistons are reset after such a pivoting action, piston return springs are arranged on the sides facing away from the pressure chambers, usually in the form of single or double helical springs.
  • the outer and the inner pressure chambers each have a separate compressed air connection, so that they can be acted upon separately with compressed air. If the pistons are to be moved inwards, ie in the direction of the drive shaft, only the external pressure chambers are subjected to compressed air. Conversely, this only happens with the internal pressure chambers.
  • the compressed air supply to the external pressure chambers takes place in the generic rotary actuators via feed channels, which are designed as bores in the housing belonging to the walls of the cylinder.
  • the feed channels are protected in this embodiment, so they can not be destroyed by external influences, as they may occur, for example, during maintenance of chemotechnical equipment.
  • the disadvantage is that the walls of the cylinder must have a thickness of strength not necessary wall thickness, so that the feed channels drilled and can be provided in the cylinder head screw holes for their attachment.
  • the drive housing for receiving the drive shaft and the cylinder are formed as a unitary casting. This not only results in a high weight and a corresponding material consumption.
  • the rotary actuator is also voluminous and therefore has a corresponding space requirement. Furthermore, high costs and complicated assembly are the result.
  • the pressure supply in this rotary actuator is not optimal. If the rotary actuator should be constructed as compact as possible, there are constraints in the cross sections of supply and outlet at the end of the feed channel, which preclude a rapid pressure build-up in the external pressure chambers.
  • the invention is based on the object, the pivot drive of the type mentioned in such a way that a quick pressure build-up can be achieved. Another task is to make the rotary actuator versatile versatility.
  • the basic idea of the invention is to lay the feed channel outwards in each case, in such a way that it is protected against damage. This is done according to the invention in that the feed channel is formed in each case as an integrally formed on the outer sides of the cylinder sleeves feed tubes. Under Anformung is to be understood that the feed tube is integral and thus material homogeneous component of the associated cylinder sleeve, so it has not been attached to her only subsequently.
  • the connection to the pressure medium connection is then done via a respective connection opening in the drive housing into which the feed channel opens.
  • the advantage of the inventive design of the pressure medium supply to the external pressure chamber is that the cross section of the respective feed channel as well as the associated outlet in the external pressure space can be made relatively free. Due to this, a much faster pressure build-up and pressure reduction in the external pressure space is possible, which is for overcoming the occasionally occurring on the piston of the rotary actuator or on the moving parts of the associated obturator slip-stick effect of advantage. In addition, the positioning times are significantly shorter.
  • the invention provides in a particularly preferred embodiment that the drive housing has at least two different sides each having a pressure medium connection with connection openings for connection to a respective feed channel, wherein each of a cylinder sleeve associated connection openings on a circle around the central axis the associated cylinder sleeve lie. Due to this, the pivoting drive according to the invention can be used in a more versatile manner, for example by providing and setting up a pressure medium connection for a flange-mounted solenoid valve arrangement and the other pressure medium connection for an attached positioner.
  • connection to the feed channel is then produced in a simple manner by rotating the cylinder sleeve about its longitudinal axis from the position in which it is connected to the first pressure medium connection via the first connection opening in such a way that it lies in alignment with the connection opening , which has connection to the second pressure medium connection.
  • the rotary actuator for both types of use can be easily set up, even on site and after installation.
  • the feed channel or the feed channels should pass through to the end of the associated cylinder sleeve and be closed at the outer end in each case with a stopper.
  • the cylinder sleeve together in the feed channel be prepared so that it retains its cross-sectional shape over its entire length.
  • the cylinder sleeve is then suitable for the production with a drawing process or by extrusion.
  • the connection between the feed channel and the associated external pressure chamber can be done by a transverse bore in the associated cylinder sleeve.
  • the respective cylinder cover is connected via at least one stud bolt, conveniently via a single stud, with the drive housing, wherein the respective stud bolt passes through the associated cylinder sleeve and the associated piston and the cylinder cover on the or the Stud is braced against the cylinder.
  • the stud can namely have relatively small diameter, because he no longer - as in the rotary actuator after the DE 10 2007 012 238 A1 - must accommodate a feed channel.
  • the cylinder (s) should respectively be braced against the drive housing via the associated cylinder cover by means of the at least one stud bolt.
  • the stud should each be coaxial with the longitudinal axis of the associated cylinder.
  • This facilitates the assembly and disassembly and in particular the rotation of the cylinder sleeve about its longitudinal axis.
  • it may be provided that in each case in the outer end of the stud bolt on the outside of the associated cylinder cover supporting clamping screw is used.
  • the kinematic connection between the piston and the drive shaft is designed in a manner known per se so that at least one rack is attached to the inner sides of the piston and the drive shaft is a pinion has, in which the rack (s) engages or border. If two cylinders are arranged coaxially to one another, the toothed racks run parallel to one another and engage the pinions on both sides.
  • the rack (s) is or are guided displaceably in the drive housing, preferably in each case in a guide recess, the guide recess (s) enclosing or enclosing the rack (s) except for cutouts in the area of the pinion.
  • the pivoting drive according to the invention is suitable for a single-acting design, in which the respective piston is supported on one side via return springs.
  • both sides of the piston can limit pressure chambers to obtain a double-acting rotary actuator.
  • the drive housing itself should have cuboid shape and be made of a solid material from which only the necessary recesses for air flow, drive shaft and mechanical guides are formed. In this way, the pressure medium consumption is reduced to a minimum because of unnecessary dead spaces.
  • the pivot drive 1 shown in all figures has a central drive housing 2, which consists of a Solid material is made.
  • the drive housing 2 has an underside 3, to which adjoin the upstanding side walls 4, 5, which extend substantially parallel to each other up to a top 6.
  • a vertically extending drive shaft 8 is rotatably mounted centrally.
  • the drive shaft 8 is freely accessible at the bottom 3 (see. FIG. 8 ).
  • She has there frontally a square socket 9, with which it can be placed on an external square of a valve or the like to form a rotationally fixed connection.
  • the drive shaft 8 is flush with the top 6 and there also has a square socket 10, over which a rotationally fixed connection can be made for example with a positioner.
  • the drive housing 2 has perpendicular to the side walls 4, 5 extending, mutually parallel and vertical end walls 11, 12, to which connect to both sides cylinder sleeves 13, 14 in a coaxial arrangement.
  • cylinder cover 15, 16 are placed on the outer ends of the cylinder sleeves 13, 14 . They are based on the outer end faces of the cylinder sleeves 13, 14 from.
  • the cylinder sleeves 12, 13 are each by a central stud 17 (he is only in FIG. 5 and to see there only in connection with the left cylinder cover 15; the attachment of the right cylinder cover 16 is mirror image) interspersed.
  • the stud bolts 17 extend coaxially to the axes of the cylinder sleeves 13, 14. They are firmly connected to the end walls 11, 12 of the drive housing 2. At their free ends, the studs 17 on the outside open blind holes 19, are screwed into the clamping screws 21, 22 from the outside through the cylinder cover 15 and 16 respectively. The heads of the clamping screws 21, 22 are on the outer sides of the cylinder cover 15 and 16, respectively. About the clamping screws 21 and 22, the bracing of the cylinder cover 15 and 16 and the cylinder sleeves 13 and 14 takes place against the drive housing. 2
  • pistons 23, 24 are used with a circular circumference. They are sealingly against the inner sides of the cylinder sleeves 13, 14 and the outer sides of the stud 17. They divide the annular spaces into external pressure chambers 25, 26 and internal pressure chambers 27, 28.
  • each double-armed racks 29, 30 formed, which extend parallel to each other and to the axis of the cylinder sleeves 13, 14, but to this by the same amount once to the left and once to the right are offset.
  • the arms of the racks 29, 30 have a substantially rectangular cross section and are axially movable in four guide channels 31, 32, 33, 34.
  • the guide channels 31, 32, 33, 34 are provided on the inside with a bearing layer, for example made of PTFE and enforce the solid material of the drive housing 2 in the horizontal direction. Since the racks 29, 30 are rigidly connected to the pistons 23, 24, the pistons 23, 24 are not guided by the cylinder sleeves 13, 14 and the stud bolts 17, but also by the racks 29, 30 safe to tilt.
  • the racks 29, 30 each have a toothing 35, 36.
  • the teeth 35, 36 are in engagement with a pinion 37 which is rotatably connected to the drive shaft 8 and is enclosed by the teeth 35, 36 on both sides. Because of these teeth 35, 36, the pistons 23, 24 can only move in opposite directions, their opposing translational movement is implemented via the existing of the teeth 35, 36 and the pinion 37 gear in a pivoting movement of the drive shaft 10 about its vertical axis.
  • a pivot limiting device 38 is provided for the drive shaft 8.
  • a symmetrical triangle 39 is placed on the lower portion of the drive shaft 8, the opposite corner projections 40, 41 has.
  • the side wall 5 are at a symmetrical distance to the center line of the drive housing 2 each have a stop screw 42, 43 screwed, the free ends of which project into the bore 7.
  • the ends form stops for the corner projections 40, 41, ie the pivotal movement of the drive shaft 8 is limited by the fact that after a certain pivot angle of the corner projections 40 and 41 abuts against the respective adjacent stop screw 42 and 43 respectively.
  • By turning the stop screws 42, 43 can be adjusted to what extent the free ends protrude into the bore 7. As a result, the pivot angle can be limited.
  • the side wall 4 has a first pressure medium mounting surface 45, on the left hand side to the inner pressure chambers 27, 28 first pressure medium opening 46 and the right side to the outer pressure chambers 25, 26 second pressure medium opening 47 are provided. From the first pressure medium opening 46, a pressure medium channel 48 initially goes perpendicular to the pressure medium mounting surface 45 inwards. At a junction 49, the pressure medium channel 48 is divided and then runs parallel to the direction of movement of the piston 23, 24. Its two ends finally open into the internal pressure chambers 27, 28 (seen only with respect to the left internal pressure chamber 27).
  • the second pressure medium opening 47 is also continued in the drive housing 2 as a pressure medium channel 50, which initially extends perpendicular to the pressure medium mounting surface 45 and then a piece down to the level according to FIG. 4 goes.
  • the pressure medium channel 50 divides and then runs parallel to the directions of movement of the pistons 23, 24. It terminates in connection openings 52, 53 in the end walls 11, 12 of the drive housing. 2
  • a second pressure medium mounting surface 54 is provided, which is flat just like the first pressure medium mounting surface 45 and which side by side has a first pressure medium opening 55 going to the inner pressure chambers 27, 28 and a second pressure medium opening 56 going to the outer pressure chambers 25, 26 (see in particular FIG. 10 ).
  • a pressure medium channel 57 goes vertically downwards and then flows into the internal pressure chambers 27, 28.
  • a pressure medium channel 58 also goes first vertically downwards to a branch 59. There, the pressure medium channel 58 divides and It then runs parallel to the direction of movement of the pistons 23, 24. It terminates in connection openings 60, 61 on the end walls 11, 12 of the drive housing (cf. FIG. 9 ).
  • the cylinder sleeves 13, 14 are each provided with an externally formed feed pipe 62, 63 which extend parallel to the direction of movement of the pistons 23, 24 over the entire length of the cylinder sleeves 13, 14. They are an integral part of the material of the cylinder sleeves 13, 14 and are with these by a drawing process been prepared.
  • a feed channel 64, 65 extends in each case within the feed pipes 62, 63.
  • the feed channels 62, 63 are closed on the cover side by plugs 66, 67. Immediately in front of the plugs 66, 67 are transverse bores 68, 69, via which the feed channels 64, 65 each have connection to the respective external pressure chamber 25 and 26 respectively.
  • the cylinder sleeves 13, 14 are mounted such that the supply channels 64, 65 are aligned with each other and with the pressure medium channel 50, so that this pressure medium channel 48 has connection to the feed channels 64, 65 and via the transverse bores 68, 69 to the external pressure chambers 25, 26.
  • connection openings 52, 53 are bridging sleeves 70, 71, which produce a kind of coupling between pressure medium channel 50 and feed channels 64, 65 and there ensure tightness.
  • the pressure medium openings 46, 47 are connected prior to startup of the rotary actuator 1 with a control valve arrangement, not shown, which is equipped with solenoid valves via the alternately a pressure medium opening 47 for supplying pressure medium of the external pressure chambers 25, 26 or the pressure medium opening 46 to the pressure medium supply of the internal pressure chambers 27, 28th can be connected.
  • a control valve arrangement not shown, which is equipped with solenoid valves via the alternately a pressure medium opening 47 for supplying pressure medium of the external pressure chambers 25, 26 or the pressure medium opening 46 to the pressure medium supply of the internal pressure chambers 27, 28th can be connected.
  • the external pressure chambers 25, 26 are then ventilated via the supply channels 64, 65 and the pressure medium channel 50 and the pressure medium opening 47.
  • the pressure medium opening 47 can be acted upon with pressure medium.
  • the external pressure chambers 25, 26 are supplied with pressure medium. This pushes the piston 23, 24 in the direction of the drive housing 2.
  • the internal pressure chambers 27, 28 are then vented via the pressure medium channel 48 and the pressure medium opening 46.
  • the positioner is placed on the upper-side pressure medium mounting surface 54.
  • the cylinder sleeves 13, 14 are after loosening the clamping screws 21, 22 from in the FIGS. 1 to 5 shown rotated position about its longitudinal axis (from FIG. 1 to FIG. 6 in a clockwise direction) until the feed channels 62, 63 are aligned with one another and with the pressure medium channel 58 (cf. FIG. 9 ). Also in this case, the coupling of pressure medium channel 58 and feed channels 64, 65 takes place by means of bridging sleeves 72, 73 at the local connection openings 60, 61.
  • the pressure medium openings 55, 56 can be acted upon by the positioner alternately with pressure medium.
  • pressure medium When pressure medium is applied via the pressure medium opening 55, the pressure medium passes into the internal pressure chambers 27, 28, so that the pistons 23, 24 are moved outwards become.
  • the external pressure chambers 25, 26 are then ventilated via the supply channels 64, 65 and the pressure medium channel 58 and the pressure medium opening 56.
  • the pressure medium opening 56 can be acted upon with pressure medium.
  • About the pressure medium channel 58 and the feed channels 64, 65 then the external pressure chambers 25, 26 are supplied with pressure medium. This pushes the pistons 23, 24 in the direction of the drive housing 2.
  • the internal pressure chambers 27, 28 are then ventilated via the pressure medium channel 75 and the pressure medium opening 55.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
EP09014559A 2009-11-23 2009-11-23 Commande pivotante Withdrawn EP2325500A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP09014559A EP2325500A1 (fr) 2009-11-23 2009-11-23 Commande pivotante
DE202010012575U DE202010012575U1 (de) 2009-11-23 2010-09-14 Schwenkantrieb

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09014559A EP2325500A1 (fr) 2009-11-23 2009-11-23 Commande pivotante

Publications (1)

Publication Number Publication Date
EP2325500A1 true EP2325500A1 (fr) 2011-05-25

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ID=42101889

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09014559A Withdrawn EP2325500A1 (fr) 2009-11-23 2009-11-23 Commande pivotante

Country Status (2)

Country Link
EP (1) EP2325500A1 (fr)
DE (1) DE202010012575U1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202015102250U1 (de) 2015-05-04 2016-08-05 H2R Automation GmbH Steuereinrichtung für Schwenkantriebe sowie Schwenkantrieb mit einer solchen Steuereinrichtung
CN109968633A (zh) * 2019-05-10 2019-07-05 郑州新生印务有限公司 Pvdc吹膜机模口碳化析出物不停机快速清除机构

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2054798A (en) * 1979-06-23 1981-02-18 Trico Folberth Ltd Fluid pressure actuators
EP0047613A1 (fr) * 1980-09-04 1982-03-17 Worcester Controls (U.K.) Limited Dispositif de génération de mouvement réciproque
DE8405693U1 (de) 1984-02-24 1984-06-07 AMG Antrieb- und Mechanik GmbH, 5000 Köln Doppelkolbenschwenkantrieb
JPH02114203U (fr) 1989-03-01 1990-09-12
DE9303955U1 (de) 1993-03-17 1993-06-03 Guo, Suh-Shin, Kao-Hsiung Getriebeeinrichtung für Druckluft- und Hydrauliksysteme
JPH06207605A (ja) 1993-01-12 1994-07-26 Atsuji Iwano トルクアクチュエータ
DE9314410U1 (de) * 1993-09-24 1994-10-13 Revo Antriebstechnik GmbH, 41812 Erkelenz Druckmittelbetätigter Stellantrieb
JP2003278712A (ja) * 2002-01-16 2003-10-02 S N Seiki:Kk エア式アクチュエータとその製造方法
DE102007012238A1 (de) 2006-03-20 2007-09-27 Wagner, Harald Schwenkantrieb

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2054798A (en) * 1979-06-23 1981-02-18 Trico Folberth Ltd Fluid pressure actuators
EP0047613A1 (fr) * 1980-09-04 1982-03-17 Worcester Controls (U.K.) Limited Dispositif de génération de mouvement réciproque
DE8405693U1 (de) 1984-02-24 1984-06-07 AMG Antrieb- und Mechanik GmbH, 5000 Köln Doppelkolbenschwenkantrieb
JPH02114203U (fr) 1989-03-01 1990-09-12
JPH06207605A (ja) 1993-01-12 1994-07-26 Atsuji Iwano トルクアクチュエータ
DE9303955U1 (de) 1993-03-17 1993-06-03 Guo, Suh-Shin, Kao-Hsiung Getriebeeinrichtung für Druckluft- und Hydrauliksysteme
DE9314410U1 (de) * 1993-09-24 1994-10-13 Revo Antriebstechnik GmbH, 41812 Erkelenz Druckmittelbetätigter Stellantrieb
JP2003278712A (ja) * 2002-01-16 2003-10-02 S N Seiki:Kk エア式アクチュエータとその製造方法
DE102007012238A1 (de) 2006-03-20 2007-09-27 Wagner, Harald Schwenkantrieb

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202015102250U1 (de) 2015-05-04 2016-08-05 H2R Automation GmbH Steuereinrichtung für Schwenkantriebe sowie Schwenkantrieb mit einer solchen Steuereinrichtung
CN109968633A (zh) * 2019-05-10 2019-07-05 郑州新生印务有限公司 Pvdc吹膜机模口碳化析出物不停机快速清除机构
CN109968633B (zh) * 2019-05-10 2023-11-24 郑州新生印务有限公司 Pvdc吹膜机模口碳化析出物不停机快速清除机构

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Publication number Publication date
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