EP1710449A1 - Vérin simple effet verrouillable - Google Patents

Vérin simple effet verrouillable Download PDF

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Publication number
EP1710449A1
EP1710449A1 EP05027442A EP05027442A EP1710449A1 EP 1710449 A1 EP1710449 A1 EP 1710449A1 EP 05027442 A EP05027442 A EP 05027442A EP 05027442 A EP05027442 A EP 05027442A EP 1710449 A1 EP1710449 A1 EP 1710449A1
Authority
EP
European Patent Office
Prior art keywords
locking
cylinder
spindle
rotation
movable
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.)
Granted
Application number
EP05027442A
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German (de)
English (en)
Other versions
EP1710449B1 (fr
Inventor
Walter Neumeister
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.)
Neumeister Hydraulik GmbH
Original Assignee
Neumeister Hydraulik 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 Neumeister Hydraulik GmbH filed Critical Neumeister Hydraulik GmbH
Priority to PL05027442T priority Critical patent/PL1710449T3/pl
Publication of EP1710449A1 publication Critical patent/EP1710449A1/fr
Application granted granted Critical
Publication of EP1710449B1 publication Critical patent/EP1710449B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/262—Locking mechanisms using friction, e.g. brake pads
    • F15B15/264—Screw mechanisms attached to the piston

Definitions

  • the invention relates to a locking cylinder according to the preamble of claim 1.
  • Such locking cylinders are the subject of four not yet published German patent applications of the protected rights holder, under the official file number 103 56 597.3 . 103 56 598.1 . 13 56 596.5 such as 10 2004 022 203.7 are guided.
  • the present patent is a further development of the above-mentioned objects of the application, so that for the sake of simplicity and to avoid repetition of the content of these four patent applications is taken in full at this point.
  • the relative to the cylinder movable locking body is pressed by means of the spring force of the spring against the counter locking body delimiting and rotating about the axis of rotation of the spindle step or tooth-shaped control edge, wherein the movable relative to the cylinder locking body and the step or the tooth are designed to be coordinated with each other such that the locking body which is movable relative to the cylinder can engage or engage in its locking position when the spindle is rotated in its first direction of rotation on the step or on the tooth in order to provide a mechanical locking to cause the spindle and wherein the control edge can run at a rotation of the spindle in its opposite, second rotational direction, substantially unhindered on the relative to the cylinder movable locking body along.
  • the spindle is thus always mechanically unlocked in this second direction of rotation.
  • the counter-locking body preferably the locking body rotatably connected to the spindle locking body, at least one outwardly open locking recess into which acted upon by the spring force of the spring and can engage relative to the cylinder movable locking body.
  • a particularly simple, space-saving and cost-effective and reliable construction can be achieved if the locking recess with a control edge-containing outlet slope, such as a ramp or inclined plane, is designed for the relative to the cylinder movable locking body.
  • a control edge-containing outlet slope such as a ramp or inclined plane
  • the locking recess has a trapezoidal cross section in the circumferential direction.
  • a locking recess can be produced in a particularly simple and cost-effective manner.
  • a particularly space-saving design in conjunction with advantageous possibilities of further improved operational safety can be achieved in that the locking recess is designed axially, ie in the longitudinal direction of the cylinder, open to the outside.
  • the locking recess is provided in a hole-disc-shaped approach, which is rotatably connected to the spindle.
  • the reliability can be further increased if a plurality of locking recesses in the circumferential direction with respect to the axis of rotation of the spindle and spaced from each other. It is particularly advantageous if at least four, preferably at least six locking recesses are provided.
  • the relative to the cylinder movable locking body is mounted parallel to the axis of rotation of the spindle axially displaceable on or in a head of the cylinder and in its locking position in an axially outwardly open locking recess or in several axially outward open locking recesses engages.
  • the locking bolt may advantageously be designed as a cylinder pin, in particular as a circular cylindrical bolt.
  • a plurality of, preferably two, locking bodies movable relative to the cylinder are designed as separately movable locking bolts.
  • Such locking bolts are simple and inexpensive to produce and require only a minimal installation and switch room, so that the space gained can be used to advantage for other elements and / or tasks or an overall smaller and lighter locking cylinder can be provided.
  • only comparatively small locking and unlocking forces are required.
  • the locking cylinder in the region of the locking unit can be made more space-saving or lighter overall. Also can be achieved by the aforementioned measures significantly reduced locking and unlocking.
  • a plurality of, preferably two, locking bodies movable relative to the cylinder are movable separately and independently of one another.
  • the relative to the cylinder movable locking body by means of a fluid working means against the spring force of the spring from its locking position can be converted into an unlocking position in which the spindle is rotatable about its axis of rotation.
  • the relatively movable relative to the cylinder locking body and thus also the spindle can be hydraulically unlocked, so that when a pressurization of the piston with fluid pressure medium, the piston can be moved with simultaneous rotation of the spindle relative to the cylinder.
  • the locking cylinder 20 shown in Figure 1 comprises a cylinder 21 and a longitudinally slidably mounted therein piston 22.
  • the piston 22 is sealed relative to the cylinder inner wall by a ring seal 68 and is on its in the direction of the longitudinal axis 29 of the cylinder 21 facing away from each other pages 44, 46 by a fluid pressure medium, preferably oil, acted upon to allow a pressure-medium-assisted movement of the piston 22 in a direction of unlocking referred to as the second direction or unlocking direction 27 or in a direction also referred to as the first direction of extension 28.
  • a fluid pressure medium preferably oil
  • the piston 22 is fixedly connected to a piston rod 23, which, starting from its end face 44 coaxial with Cylinder longitudinal axis 29 extends.
  • the cylinder 20 is closed at its the free end 67 of the spindle 35 side by a piston rod 23 receiving cover 30.
  • the cylinder 21 is fixedly connected to a step-shaped projection 66. This is in turn completed by a cylinder bottom 53 forming lid or head 31.
  • the piston 22 forms a projection 32 which is non-rotatably connected to the piston rod 23.
  • the piston 22 is designed as a tubular hollow body and has an internal thread 34, also referred to as a piston thread. This is engaged with an external thread 36, also referred to as a spindle thread, of a spindle 35 on which the piston 22 is guided.
  • the internal thread 34 of the piston 22 and the external thread 36 of the spindle 35 are preferably designed as eight-speed trapezoidal coarse thread, which together form a non-self-locking thread 37, which is designed here right-handed.
  • the piston rod 23 For attachment of the locking cylinder 20, the piston rod 23 at its free end a here designed with an eyelet fastener 25, and a correspondingly shaped fastener 26 is mounted opposite to the head 31 of the cylinder 21.
  • the pressure medium can be fed via the channels 48 and 49 on both sides 44 and 46 of the piston 22 into a first working chamber 45 and into a second working chamber 33 in order to achieve a movement of the piston 22 along the cylinder 21 in the retraction direction 27 or in the extension direction 28 can.
  • the first working chamber 45 against the second working chamber 33 sealed via the annular seal 68 of the piston 22.
  • the plate springs 134 and the plate springs 136 are each alternately successively preferably arranged such that in each case the spring travel of each plate spring 134, 136 is available for a resilient mounting of the spindle 35.
  • the plate springs 134, 136 are selected with regard to their spring characteristics and arrangement such that in the regular driving operation, when the piston 22 is moved in the retraction direction 27, the thereby transmitted via the non-self-locking thread 37 and the spindle 35 dynamic resultant forces, d. H. be compensated so that the support body 124 is always lifted from the head 31 of the cylinder bottom of the cylinder 21.
  • the flange-shaped projection 65 is provided on the transverse to the axis of rotation 43 of the spindle 35 extending wall part 79 or perforated disc part 141 with here a total of six locking recesses 38.1 to 38.6.
  • the locking recesses 38.1 to 38.6 are each arranged at the same angular intervals on an imaginary circumferential circle 78 such that two locking recesses are arranged diametrically opposite each other.
  • each locking recess 38.1 to 38.6 has a trapezoidal cross section 139 in the sectional plane shown in FIG.
  • a stepped or tooth-shaped control edge 78 is formed, which is characterized in the view of Figure 3 by a dash-dotted circle concentric with the axis of rotation 43 of the spindle 35 is arranged. A part of this control edge 78 is clearly visible in the cross section according to FIG.
  • Each locking recess 38; 38.1 to 38.6 is designed with conically inwardly tapering wall portions 70 and serves to receive outwardly conically tapered wall parts 72 of locking bolt 40; 40.1, 40.2.
  • the conical tapered wall parts 72 having free end 57 of the respective locking pin 40 is preferably designed so matched to the locking recesses 38 in the region of their conically tapered wall parts 70, that a fürströmspalt 71 is formed for the pressure medium.
  • This fürströmspalt 71 is in fluid communication with a gap 91 which is arranged in the region of the radial edges of both the flange-shaped projection 65 and the opposite part of the head 31 of the cylinder 21.
  • This gap 91 is in fluid communication with a switching channel 47, which in turn Fluid connection with channels 48 and 49 can be brought, via which the piston 22 can be acted upon on its respective sides 44 and 46 with pressure medium.
  • the locking bolts 40 are designed cross-sectionally closed in the region of their free ends 57.
  • Each locking bolt 40 is designed as a preferably elongated cylinder pin 69 rotationally symmetrical to its longitudinal axis 74.
  • Each locking bolt 40 has a circular cylindrical outer contour 50 and a circular cylindrical inner contour, so it is designed as a rotary hollow body.
  • Each locking bolt 40 also has a circular cylindrical recess 92 which is designed with parallel to the longitudinal axis 74 of the respective locking bolt 40 delimiting wall parts and which is open to the head 31 of the cylinder 21 opposite end 56 to the outside. This recess 92 serves to receive and lateral support of a designed as a compression spring spring 39.
  • the spring 39 is supported with one of its ends 95 on an inner surface 94 of a radially inwardly extending support and abutment surface 60 of the locking bolt 40.
  • the other end 96 of the spring 39 is supported on an inner surface of a corresponding support and contact stage 76 of the head 31 of the cylinder 21.
  • a radially outwardly extending abutment and counter-sealing surface 98 is provided for the locking bolt 40, which is arranged perpendicular to the wall portions bounding the bearing recess 75. Every locking bolt 40 has at its head or spring-side end 59 on a ring end edge 99, which is designed with a circumferential annular sealing surface 97 and in the unlocking 27 of the respective locking bolt 40 has.
  • This annular sealing surface 97 is sealingly against the likewise circumferential abutment and counter-sealing surface 98 of the head 31 of the cylinder 21, when the respective locking pin 40 has been transferred to a loading with the force exerted by the pressure medium in unlocking 27 compressive forces in its unlocked position. Under the then effective pressure forces a seal is achieved there, so that no leakage of pressure fluid along the outer surfaces of the respective locking bolt 40 occurs.
  • the abutment and Abdichtalle construction 96 advantageously limits the respective Entriegelungshub the locking pin 40th
  • Each locking bolt 40 is slidably mounted parallel to the axis of rotation 43 of the spindle 35 with little play in the cylindrical inner contour 98 having bore or bearing recess 75, so starting from the locking position 41 shown in Figures 1 and 2 by means of the pressure medium in extension or Unlocking direction 28 against the spring forces of the spring 39 are moved to its unlocked position, or vice versa after pressure relief in the region of its free locking end 57 of its unlocked position automatically, ie by the force exerted by the respective spring 39 on the respective locking pin 40 return spring forces, be transferred back into its locking position 41.
  • the bearing recess 75 thus has an inner diameter which is slightly larger than the outer diameter of the locking bolt 40.
  • the locking bolt 40 has at its free end 57 a perpendicular to its longitudinal axis 74 arranged active surface 58 on which the fluid pressure medium can act to transfer the locking pin 40, starting from the locking position 41 shown in Figure 2 in an unlocking position, in which he is out of engagement with the locking recesses 38.1 to 38.6, so no rotation of the spindle 35 in its first direction of rotation 51 is no longer blocked.
  • the oil located in the associated locking recesses 38 is displaced via the switching channel 47 into the return channel 87.
  • FIG. 5 is a hydraulic circuit diagram is illustrated, with particularly advantageous control means and ways are used. It is provided as a load-holding Senkbrems means 150 designated load holding Senkbrems valve, which causes when pressurizing the piston 22 on its second side 44 with the in the second working chamber 45 pressure fluid to form a working pressure, the displacement of the Piston 22 causes in a direction of retraction also referred to as the second direction 27, at the same time in the first working chamber 33 on the first side 46 of the piston 22, a counter-pressure exerted by the pressure medium located in the first working chamber 33 acts. This counter-pressure is less than the working pressure in the second working chamber 45, so that an uncontrolled advance of the piston 22 in the second direction 27 is avoided.
  • load-holding Senkbrems means 150 designated load holding Senkbrems valve
  • the load-holding lowering brake means 150 blocks a return flow of the pressure medium from the working chamber 33, so that the piston 22 is held securely in the desired stroke position by the pressure medium in the working chamber 33.
  • the load hold counterbalance valve 150 has an inlet 153, an outlet 154, and a pressure fluid control port 155, the inlet 153 being fluidly connected to the first working chamber 33 via the channel 49.
  • the control port 155 of the load-holding lowering valve 150 is fluidly connected to the return passage 87.
  • a gearströmsperrkar 156 is fluidly connected, which allows a flow of the pressure medium from the outlet 154 to the inlet 153, but blocks in the opposite direction.
  • supply channel 86 branches off into the channel 55 opening channel in which a blocking in this direction check valve 82 is arranged.
  • the channel 48 and the switching channel 88 return channel 87 branches off also into the channel 55 emptying channel, in which also a blocking in this direction check valve 83 is arranged.
  • the locking cylinder 20 shown in the figures is designed for locking under pressure. This means that the locking cylinder 20 for moving or lifting a not closer shown in the figures.
  • Load in the extension direction 27 is used. Act through the to be moved or lifted load on the piston rod 23 against the extension direction 28 acting compressive forces. If the piston rod 23 is to be held under load in any desired position in any desired lifting or extension position, the piston rod 23 is in a stable position with its piston 22 in the desired lifting or extended position by the load-holding lowering valve 150 kept hydraulically secured to the cylinder 21.
  • a kind of pawl mechanism 54 is thus realized, by means of which a mechanical locking of the spindle 35 in a first direction of rotation 51 about its axis of rotation 43 is reached, while the spindle 35 in its opposite second direction of rotation 52 about its axis of rotation 43 substantially free is movable or remains, in particular to allow movement of the piston 22 along the cylinder 21, here in the extension direction 28.
  • the invention is not only applicable to pressure-locking locking cylinders, but of course also in lock locking on locking cylinders.
  • the load-holding counterbalance valve 150 would not be associated with the flow channel 86, as shown in FIG. 5, but would be associated with the return channel 87.
  • the outlet 154 of the load-holding lowering valve 150 would be fluidly connected to the return passage 87 and the inlet 153 of the load-holding lowering valve 150 would be fluidly connected to the channel 48 opening into the second working chamber 45.
  • the switching channel 47 would then not open into the opening into the second working chamber 45 channel 48, but the switching channel 47 in the opening into the first working chamber 33 channel 49. The rest of the construction could remain unchanged.
  • the pressure medium can then flow from the channel 86 via the flow restrictor 173, which is continuous in this direction, into the channel 49, which in turn opens into the first working chamber 33.
  • the piston 22 is acted upon by pressure on its second side 46, so that a force in the extension direction 28 acts on the piston 22.
  • the here designated return channel 87 channel is acted upon with pressure medium, d. H. It is fed by means of the pump not shown in detail by the return passage 87, a pressure medium. This increases the pressure in the downstream channels, i. H. in the switching channel 88 for the load-holding Senkbrems valve 150, in the switching channel 47 for the hydraulic actuation of the locking pin 40 and in the opening into the second working chamber 45 channel 48 at.
  • the load-holding lowering brake valve 150 is adjusted by a spring pressure so that it opens only above a certain pressure, from which therefore the pressure medium can flow from the inlet 153 to the outlet 154 of the load-holding Senkbrems valve 150.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
EP05027442A 2005-04-08 2005-12-15 Vérin simple effet verrouillable Active EP1710449B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL05027442T PL1710449T3 (pl) 2005-04-08 2005-12-15 Cylinder ryglujący jednostronnego działania

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005016090A DE102005016090B4 (de) 2005-04-08 2005-04-08 Einfach wirkender Verriegelungszylinder

Publications (2)

Publication Number Publication Date
EP1710449A1 true EP1710449A1 (fr) 2006-10-11
EP1710449B1 EP1710449B1 (fr) 2007-11-28

Family

ID=36659971

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05027442A Active EP1710449B1 (fr) 2005-04-08 2005-12-15 Vérin simple effet verrouillable

Country Status (4)

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EP (1) EP1710449B1 (fr)
DE (3) DE102005016090B4 (fr)
ES (1) ES2297599T3 (fr)
PL (1) PL1710449T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1995471A2 (fr) 2007-05-25 2008-11-26 Neumeister Hydraulik GmbH Cylindre verrouillable à palier fluidique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013102167B4 (de) 2013-03-05 2022-01-05 Ewo Fluid Power Gmbh Hydraulikzylinder mit redundantem Sicherheitsventilsystem

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1356596U (fr)
US3442176A (en) * 1967-05-01 1969-05-06 Gen Electric Actuator locking mechanism
US4293115A (en) * 1979-09-24 1981-10-06 Hydril Company Testing mechanism for blowout preventer ram lock
US4481864A (en) * 1981-07-21 1984-11-13 Selenia Industrie Elettroniche Associate S.P.A. Hydraulic jack with mechanical safety lock
EP0536954A1 (fr) * 1991-10-10 1993-04-14 Lucas Industries Public Limited Company Dispositif de verrouillage d'un inverseur de poussée
EP1106841A2 (fr) * 1999-12-07 2001-06-13 Weber-Hydraulik GmbH Actionneur de positionnement linéaire
DE10356597B3 (de) 2003-12-04 2005-06-02 Neumeister Hydraulik Gmbh Verriegelungszylinder
DE10356598B3 (de) 2003-12-04 2005-06-02 Neumeister Hydraulik Gmbh Verriegelungszylinder
DE102004022203B3 (de) 2004-05-05 2005-08-11 Neumeister Hydraulik Gmbh Verriegelungszylinder mit Gewinde-Freilauf

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10356596B3 (de) * 2003-12-04 2005-06-02 Neumeister Hydraulik Gmbh Verriegelungszylinder

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1356596U (fr)
US3442176A (en) * 1967-05-01 1969-05-06 Gen Electric Actuator locking mechanism
US4293115A (en) * 1979-09-24 1981-10-06 Hydril Company Testing mechanism for blowout preventer ram lock
US4481864A (en) * 1981-07-21 1984-11-13 Selenia Industrie Elettroniche Associate S.P.A. Hydraulic jack with mechanical safety lock
EP0536954A1 (fr) * 1991-10-10 1993-04-14 Lucas Industries Public Limited Company Dispositif de verrouillage d'un inverseur de poussée
EP1106841A2 (fr) * 1999-12-07 2001-06-13 Weber-Hydraulik GmbH Actionneur de positionnement linéaire
DE10356597B3 (de) 2003-12-04 2005-06-02 Neumeister Hydraulik Gmbh Verriegelungszylinder
DE10356598B3 (de) 2003-12-04 2005-06-02 Neumeister Hydraulik Gmbh Verriegelungszylinder
DE102004022203B3 (de) 2004-05-05 2005-08-11 Neumeister Hydraulik Gmbh Verriegelungszylinder mit Gewinde-Freilauf

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1995471A2 (fr) 2007-05-25 2008-11-26 Neumeister Hydraulik GmbH Cylindre verrouillable à palier fluidique

Also Published As

Publication number Publication date
DE202005021379U1 (de) 2007-12-20
ES2297599T3 (es) 2008-05-01
PL1710449T3 (pl) 2008-05-30
EP1710449B1 (fr) 2007-11-28
DE102005016090B4 (de) 2007-02-22
DE502005002102D1 (de) 2008-01-10
DE102005016090A1 (de) 2006-10-12

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