EP1538343A2 - Vérin verrouillable - Google Patents

Vérin verrouillable Download PDF

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Publication number
EP1538343A2
EP1538343A2 EP04025023A EP04025023A EP1538343A2 EP 1538343 A2 EP1538343 A2 EP 1538343A2 EP 04025023 A EP04025023 A EP 04025023A EP 04025023 A EP04025023 A EP 04025023A EP 1538343 A2 EP1538343 A2 EP 1538343A2
Authority
EP
European Patent Office
Prior art keywords
locking
load
outlet
pressure
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.)
Granted
Application number
EP04025023A
Other languages
German (de)
English (en)
Other versions
EP1538343A3 (fr
EP1538343B1 (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 PL04025023T priority Critical patent/PL1538343T3/pl
Publication of EP1538343A2 publication Critical patent/EP1538343A2/fr
Publication of EP1538343A3 publication Critical patent/EP1538343A3/fr
Application granted granted Critical
Publication of EP1538343B1 publication Critical patent/EP1538343B1/fr
Anticipated expiration legal-status Critical
Active 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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/261—Locking mechanisms using positive interengagement, e.g. balls and grooves, for locking in the end positions
    • 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
    • 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
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B2015/1495—Characterised by the construction of the motor unit of the straight-cylinder type with screw mechanism attached to the piston

Definitions

  • the invention relates to a locking cylinder with a cylinder and a piston using a fluid Pressure medium movable parallel to the longitudinal axis of the cylinder is, and which is provided with a piston thread, the with the formation of a non-self-locking thread with a spindle thread of a spindle is engaged, the around a parallel to the longitudinal axis of the cylinder arranged Rotary axis is rotatable and the at least one outward has open locking recess, in the at least an acted upon by spring force of a spring Locking body can engage, against rotation secured around the axis of rotation of the spindle and relative to the Cylinder is mounted movably and by means of the Spring force of the spring in a locking position is convertible, in which he is in the locking recess the spindle engages, so that then a rotation of the Spindle is blocked around its axis of rotation, and where the Locking body using a fluid working medium against the spring force of the spring from the locking position in an unlocking position
  • Such a locking cylinder is known from JP 083 034 10 A became known.
  • a locking body large-volume locking piston provided by the central Through hole, a shaft of a ball screw extends and with a variety of concentric to Spindle arranged and towering along the spindle Teeth is integrally connected.
  • the teeth of the locking piston engage with opposite teeth of a gear rotatably with this concentrically receiving spindle is connected.
  • a kind of toothed coupling is formed.
  • the Locking piston points at his pointing away from the teeth Side a hollow section with an internal toothing, and the tooth flanks of the teeth of the internal teeth extend parallel to the axis of rotation of the spindle.
  • the Internal gearing is engaged with a matching External toothing of a pinion, fixed with a End cover of the cylinder is connected.
  • the locking piston is parallel to the axis of rotation of Ball screw displaceable, but against rotation around stored the spindle axis blocked.
  • a circumferential Seal On the outer circumference of the locking piston is a circumferential Seal provided, which can be acted upon by a pressure medium Pressure medium space towards the end cap of the cylinder seals.
  • This construction of a locking unit is expensive and takes up comparatively much space.
  • the locking piston must be at his Outer circumference sealed with a circumferential seal what happens when moving the locking piston for the purpose the locking or unlocking to corresponding frictional forces leads, reducing the efficiency of this locking cylinder is limited.
  • the ball screw is so on the cylinder over a Ball bearing and one at the free end of the spindle shaft mounted plain bearing clamped clamped that a Movement of the spindle in the longitudinal direction of the cylinder is not is possible while rotating the spindle around its Longitudinal axis is possible.
  • This is supported by the free end of the spindle shaft sliding on an inner surface of the End cap of the cylinder and the ball bearing is by means of an external thread of the ball screw screwed nut against a transverse to the cylinder running paragraph fixed.
  • This construction is limited to applications in which only comparatively small loads can be raised. For larger loads, however, it can cause wear come to the feeding of the plain bearing. It can to Formation and detachment of metal shavings or particles come, which the function of the locking unit to a blockade of the Locking piston. This means an unacceptable security risk.
  • the control of the locking piston having locking unit and controlling the movement of the piston take place in this construction via mechanically coupled Directional valves such that when lifting or in the Lowering the load to an undesirable lead of the Pistons can come. This means a difficult to control Piston movement. Especially at elevated pressures or Piston velocities may cause cavitation at the Piston seal and the piston rod come, what a Security risk means and what life span limited accordingly.
  • the lock cylinder comprises a cylinder and a Piston, using one of two sides of the piston deliverable fluid pressure medium parallel to the longitudinal axis the cylinder is movable and the one with a piston thread that is under training one not self inhibiting thread with a spindle thread of a spindle is engaged, which is parallel to the longitudinal axis of the Cylinder arranged axis of rotation is rotatable and the at least one outwardly open locking recess in which at least one by means of a spring force Spring can engage engaged locking body, the against rotation about the axis of rotation of the spindle secured and axially parallel to the axis of rotation of the spindle slidably mounted on a head of the cylinder, and the spring force of the spring in a locking position is convertible, in which he in the Locking recess of the spindle to form a positive and bidirectional locking of the Spindle engages, so that then rotation of the spindle to its axis of rotation in opposite directions of rotation is blocked and where
  • the locking bolts move independently of each other are arranged, ie in particular without mechanical Forced coupling between the locking bolts.
  • the locking bolts move independently of each other are arranged, ie in particular without mechanical Forced coupling between the locking bolts.
  • only uses two separate locking bolts become. This eliminates the risk of tilting or Further reduce deadlocks.
  • the locking bolt respectively in one towards the side of the locking recesses open bearing recess of the head of the cylinder with are stored small game.
  • the Locking bolt when it comes to the Locking bolt is about cylinder pin, the preferably have a circular cylindrical outer contour. It may therefore be particularly advantageous if the Locking bolts at their free locking ends each have a conical outer contour and / or if the cylinder bolts each in a cylindrical Inner contour bearing recess with little play are stored.
  • the locking bolts each one to their, the respective spring associated end open to the outside Have recess in which each as a compression spring designed spring is received with a spring section and there with one of their ends at each one Supported inside surface of the respective locking bolt is, with her other end to the head of the cylinder is supported.
  • the locking bolts each have a circumferential Have sealing surface in the unlocking of the has respective locking bolt, and in the Unlocking position of the respective locking bolt and then under the working means in the unlocked position exerted compressive forces on a rotating Sealing surface of the head of the cylinder sealing is applied.
  • the sealing surface at the same time a stop surface for Limitation of an unlocking stroke of the respective Locking bolt trains.
  • the sealing surface in the area of the spring associated end of the locking bolt is arranged.
  • sealing surface at an annular end edge of the locking bolt at the spring associated End is arranged.
  • the locking bolt cross-section are designed so that closed at the respective Sealing surface of sealingly abutting sealing surface of respective locking bolt leakage of the working fluid along the respective locking bolt is prevented.
  • the locking bolts each one Passage channel, which in the locked position in the region of the locking recess, preferably in the Locking recess opens and the other end with a preferably connected as a discharge channel serving channel is, so that the fluid working fluid in one movement the respective locking bolt from its unlocked position in its locking position from the respective locking recess in the aforementioned Channel can flow.
  • the respective passage to his the locking recess associated end of the respective locking bolt a flow area which is much smaller than an effective area of the respective locking bolt on which the fluid Working means can attack to the respective locking bolt to convert into its unlocked position.
  • the lock cylinder comprises a cylinder and a Piston, parallel by means of a fluid pressure medium to the longitudinal axis of the cylinder is movable and with a Piston thread is provided, the formation of a non-self-locking thread with a spindle thread a spindle is engaged, which is parallel to a Rotary axis arranged along the longitudinal axis of the cylinder is rotatable and the at least one outwardly open locking recess has, in the at least one by means of spring force engage a spring acted on locking body can, against a rotation about the axis of rotation of the spindle secured and axially parallel to the axis of rotation of the spindle slidably mounted on a head of the cylinder, and the spring force of the spring in a locking position is convertible, in which he in the Locking recesses of the spindle engages, so that then blocks rotation of the spindle about its axis of rotation is and wherein the locking body using a fluid working fluid against the spring force
  • the support body at its free end has a support surface located on an opposite Supporting surface of the head of the cylinder is supported, if the support body in the second direction on the spindle absorbs acting axial forces and preferably on the Cylinder transfers.
  • Such an advantageous support especially in case of overload or damage occur.
  • the support body at a Actuation of the spindle in the second direction with an overload axial force that is equal to or greater than as the limit axial force on the support surface of the head of the Cylinder supported, whereby the overload axial forces be transferred to the cylinder or compensated there.
  • the support body as a cylinder bolt is designed.
  • the support body coaxial with the axis of rotation the spindle is arranged.
  • the second thrust bearing on the Support body is added.
  • the second thrust bearing as a needle bearing is designed.
  • the second thrust bearing one opposite a bearing capacity of the first thrust bearing smaller Carrying capacity.
  • first thrust bearing a first Ring bearing forms with a first bearing diameter and that the second thrust bearing with a second ring bearing forming a second supporting diameter, the smaller is considered the first bearing diameter of the first Ring bearing.
  • the spring with a plate spring is designed.
  • the spring under training of a Disk spring package is designed with several disc springs.
  • the plate spring or the disc springs is received on the support body or are.
  • the support body, the thrust bearing and the spring is arranged coaxially with the axis of rotation of the spindle are.
  • the locking body as a locking bolt is designed.
  • the lock cylinder comprises a cylinder and a Piston, using a two sides of the piston in a first working chamber and a second working chamber deliverable fluid pressure medium parallel to the longitudinal axis of the cylinder is movable, and that with a piston thread that is under formation of a non-self-locking Thread with a spindle thread of a spindle in Engaging, which is parallel to the longitudinal axis of the Cylinder arranged axis of rotation is rotatable and the at least one outwardly open locking recess in which at least one by means of a spring force Spring can engage engaged locking body, the against rotation about the axis of rotation of the spindle secured and firmly connected to the cylinder, however is mounted relative to this movable, and the help the spring force of the spring in a locking position is convertible, in which he is in the locking recess the spindle engages, so that then a rotation of the Spindle is blocked around its axis of rotation, and where the Locking body using a fluid working
  • the load-holding lowering brake means controlled backpressure depending on the respective one Move the piston along the cylinder Working pressure is controlled.
  • the load-holding lowering brake means controlled backpressure depending on the respective one Move the piston along the cylinder Working pressure is controlled, so with increasing Working pressure of the simultaneously acting back pressure decreases.
  • the back pressure is inversely proportional to the Working pressure is controlled.
  • the load-holding lowering brake means each one first inlet for the pressure medium, an outlet for the Pressure medium and a control connection for the pressure medium wherein the inlet of the first load-holding lowering brake means fluidly connected to the first working chamber and the inlet of the second load-holding lowering brake means is fluidly connected to the second working chamber, and wherein the outlet of the first load-holding lowering brake means to the control terminal of the second load-holding lowering brake means fluidly connected and the outlet of the second load-holding lowering brake means with the control terminal the first load-holding lowering brake means is fluidly connected, and wherein with the inlet and the outlet of the respective Load-holding lowering brake means each a remindströmsperrstoff fluidly connected, each having a flow of the Pressure medium from the outlet to the inlet of the respective Load-holding lowering brake agent allows, but one opposite direction respectively locks, and that optionally the outlet of the first load-holding lowering brake means and thus the control terminal of the second Load-holding lowering brake
  • the outlet of the first load-holding lowering brake means or the outlet of the second load-holding lowering brake means in fluid communication with the locking body or the locking bodies can be brought, so that upon expelling the outlet of the first Load-holding lowering brake means or the outlet of the second Load-holding lowering brake fluid with pressure medium, this the Supplied locking body or the locking bodies is to this or this in his or her unlocking position to convict.
  • a preferred embodiment can be provided be that between the outlet of the first load-holding lowering brake means and the outlet of the second load-holding lowering brake means at least one remindströmsperrstoff is arranged, when an admission of the outlet the first load-holding lowering brake means with pressure medium a Pressure fluid flow to the outlet of the second load-holding lowering brake means prevented and vice versa an admission of the outlet of the second load-holding lowering brake means with pressure medium, a pressure medium flow towards the outlet of the first load-holding lowering brake means prevented, and in both cases a supply of the Pressure medium to the locking body or the locking bodies so that this or this in his or their unlocked position is or will be transferred.
  • the remindströmsperrstoff a first inlet for the pressure medium, a second inlet for the Having pressure medium and an outlet for the pressure medium, wherein the first inlet of the remindströmsperrstoffs with the Outlet of the first load-holding lowering brake fluidly connected and wherein the second inlet of the remindströmsperrstoffs with the outlet of the second load-holding lowering brake means fluidly connected, and wherein the first inlet of the remindströmsperrstoffs and the second inlet of the remindströmsperrstoffs connected to each other via a fluid channel are in the one with the outlet of the remindströmsperrstoffs connected fluid channel opens at a confluence point, so that from the confluence a first channel part of the Fluid channel and a second channel part of the fluid channel branches off, and wherein a locking member for shutting off the first Channel part or the second channel part is provided, and wherein in the shut-off state of the second channel part of the first inlet of the remindströmsperrstoffs, the first Channel part
  • the remindströmsperrstoff a first inlet for the pressure medium, a second inlet for the Having pressure medium and an outlet for the pressure medium, wherein the first inlet of the remindströmsperrstoffs with the Outlet of the first load-holding lowering brake fluidly connected and wherein the second inlet of the remindströmsperrstoffs with the outlet of the second load-holding lowering brake means fluidly connected, and wherein the first inlet of the remindströmsperrstoffs and the second inlet of the remindströmsperrstoffs connected to each other via a fluid channel are in the one with the outlet of the remindströmsperrstoffs connected fluid channel opens at a confluence point, so that from the confluence a first channel part of the Fluid channel and a second channel part of the fluid channel branches off, and wherein a first locking member for shutting off the first channel part and a second locking member for shutting off the second channel part is provided, which is the first Channel part and the second channel part with respect to a Pressure fluid flow from the outlet
  • the working fluid or the pressure medium the Supplied locking body or the locking bodies is to this or this in his or her unlocking position to convict and that at the same time the Pressure medium either the first working chamber or the second working chamber is supplied to a movement of the Piston in the first direction or in the second direction to effect.
  • the work equipment or the pressure medium first the locking body or the locking bodies is fed to this or these in his or her To transfer unlocking position and that then the Pressure medium either the first working chamber or the second working chamber is supplied to a movement of the Piston in the first direction or in the second direction to effect.
  • the respective remindströmsperrstoff a Locking member for preventing a pressure fluid flow of the Inlet to the outlet of the respective load-holding lowering brake means characterized by the spring forces of a spring is acted upon, so that opening the remindströmsperrstoffs and thus a flow of pressurized fluid from the outlet to the inlet of the respective load-holding lowering brake means only after exceeding a limit pressure of the pressure medium whose value is determined by a spring characteristic of the depends on each spring.
  • the locking cylinder 20 shown in Figure 1 comprises a cylinder 21 and a longitudinally displaceable therein mounted piston 22.
  • the piston 22 is opposite to Cylinder inner wall sealed 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 a pressure fluid assisted movement of the piston 22 in one as a second direction or unlocking designated retraction direction 27 or in one as well first direction designated extension direction 28 to enable.
  • 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 on its the free end 67 of the spindle 35 associated side by a piston rod 23 receiving the lid 30th completed.
  • On its other side is the cylinder 21st firmly connected to a step-shaped projection 66. This is in turn by a cylinder bottom 53 forming Cover or head 31 completed.
  • the piston 22 forms a projection 32, the rotation with the Piston rod 23 is connected.
  • the piston 22 is as a designed tubular body and also has a Piston thread designated internal thread 34. This is engaged with a spindle thread as well designated external thread 36 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 an eight-speed trapezoidal steep thread that together form a non-self-locking thread 37.
  • the Piston rod 23 For attachment of the locking cylinder 20, the Piston rod 23 at its free end one here with an eyelet designed fastener 25, and a corresponding designed fastener 26 is opposite attached to the head 31 of the cylinder 21.
  • the pressure medium is via the channels 48 and 49 on both Pages 44 and 46 of the piston 22 in a first working chamber 45 and in a second working chamber 33 can be fed to a Movement of the piston 22 along the cylinder 21 in Retraction direction 27 or in the extension 28 to reach can.
  • Thrust bearing 121 in the form of a second ring bearing 130th provided at the head end 77 of the spindle 35th is arranged.
  • This thrust bearing 121 is also as a Rolling 122 designed in the form of a needle bearing 123. It is fixed on a coaxial with the axis of rotation 43 of the spindle 35 with the spindle 35 connected support body 124 in the form a cylinder pin 125 is added, extending in the direction the cylinder bottom or head 31 of the cylinder 21st extends and the coaxial with the axis of rotation 43 spindle 35th is arranged.
  • the disc springs 134 and the disc springs 136th in each case alternately one after the other, preferably in such a way arranged that in each case the spring travel of each plate spring 134, 136 for a resilient mounting of the spindle 35 for Available.
  • the disc springs 134, 136 are in terms their spring characteristics and arrangement chosen such that in the regular driving operation, when the piston 22 in Einfahrcardi 27 is moved, it does not over the self-locking thread 37 and the spindle 35 transmitted collected dynamic resulting forces, d. H. be compensated so that the support body 124 always from lifted off the head 31 of the cylinder bottom of the cylinder 21 is.
  • the wear the used disc springs 134 and 136 bill, so that when exposed to the overload axial forces a displacement of the spindle 35 in the retraction direction 27 while simultaneously squeezing the Disc springs 134, 136 occurs until the support body 124 with the existing at its free end support surface 129 the opposite support surface 131 of the head 31 of the Cylinder rests.
  • the support body 124 is therefore supported then there, so that the acting overload axial forces then from the spindle 35 via the support body 124 on the Head 131 of the cylinder 21 are transferred without that the needle bearing 123 would be damaged.
  • Disc springs 134, 136 Due to the arrangement and the selected spring characteristics of Disc springs 134, 136 is therefore a certain force given, that of a certain limit axial force corresponds, when it falls below the support body 124th is lifted and when they reach or exceed a displacement of the spindle 35 together with the Support body 124 in retraction 27 occurs until the Support body 124 bears against the head 31 of the cylinder 21.
  • the flange-shaped projection 65 is at the transversely to the Fulcrum 43 of the spindle 35 extending wall portion 79 with here a total of eight locking recesses 38.1 to 38.8 provided, which open to the cylinder bottom 53 toward the outside are.
  • the locking recesses 38.1 to 38.8 are in each equal angular distances from each other on a imaginary circumference circle arranged such that each two Locking recesses arranged diametrically opposite each other are and therefore on a rotation axis 43 of the spindle 35th containing straight lines are arranged.
  • Each locking recess 38 is conically tapering inwards Wall parts 70 designed and used to accommodate yourself outwardly conically tapered wall parts 72 of Locking bolt 40, 140.
  • This fürströmspalt 71 is in fluid communication with a gap 91 in the region of the radial edges both the flange-shaped projection 65 as well as this opposite part of the head 31 of the cylinder 21st is arranged.
  • This gap 91 is in fluid communication with a switching channel 47, which in turn in fluid communication with channels 48 and 49 can be brought, via which the piston 22nd on its respective pages 44 and 46 with pressure medium can be acted upon.
  • a first embodiment of a locking bolt 40 is shown in Figures 1 and 2 and a second embodiment of a locking bolt 140th is illustrated in FIG.
  • the locking bolt 40 is in contrast to the locking bolt 140 in Area of its free end 57 cross-sectionally closed designed while the locking bolt 140 as a hole nozzle 90 with an open to his free end 57 and concentric with its longitudinal axis 74 designed passageway 54 is provided. Except for this passage 54, however, the locking bolts 40 and 140 are identical designed, wherein like reference numerals like elements affect.
  • Each locking bolt 40, 140 is preferred as one elongated cylinder pin 125 rotationally symmetrical to designed its longitudinal axis 74. Every locking bolt 40, 140 has a circular cylindrical outer contour 50 and a circular cylindrical inner contour, so is as a Rotational hollow body designed. Every locking bolt 40, 140 also has a circular cylindrical recess 92 on, with parallel to the longitudinal axis 74 of the respective Locking bolt 40, 140 delimiting wall parts is designed and the to the head 31 of the cylinder 21st opposite end 56 is open to the outside. These Recess 92 serves for receiving and lateral support a designed as a compression spring spring 39. This is in mounted state with a spring portion 93 in the Recess 92 recorded.
  • the spring 39 is supported with one of its ends 95 on an inner surface 94 of a radially inwardly extending support and conditioning stage 60 of the locking bolt 40, 140 from.
  • the other end 96 of the Spring 39 is supported on an inner surface of a corresponding one Support and conditioning stage 76 of the head 31 of the Cylinder 21 off.
  • a radially outwardly extending stop and Mating surface 98 for the locking bolt 40, 140 provided perpendicular to the bearing recess 75th limiting wall parts is arranged. Every locking bolt 40, 140 has at its head or spring side End 59 a ring end edge 99, which with a circumferential ring-sealing surface 97 is designed and the in Unlocking 27 of the respective locking bolt 40, 140 points.
  • This ring sealing surface 97 is located sealing on the likewise circumferential stop and Mating surface 98 of the head 31 of the cylinder 21, when the respective locking bolt 40, 140 after a Actuation with the pressure medium in unlocking 27 exerted pressure forces in his Unlocking position has been transferred. Under the then effective pressure forces a sealing is achieved there, so no leakage of pressure fluid along the Outer surfaces of the respective locking bolt 40, 140th occurs.
  • the stop and sealing counter surface limits 96 advantageous the respective Entriegelungshub the Locking bolt 40, 140.
  • Each locking pin 40, 140 is with little play in the cylindrical inner contour 98 having a bore or bearing recess 75 parallel to the axis of rotation 43, the Spindle 35 slidably mounted, so it can be based on the locking position shown in Figures 1, 2 and 4 41 in the extension or unlocking direction 28 using the pressure medium against the spring forces of the spring 39 in its unlocked position can be moved, or can vice versa after pressure relief in the area of its free Locking end 57 of its unlocked position automatically, d. H. by the spring 39th on the respective locking bolt 40, 140 exerted Return spring forces, again in its locking position 41 are transferred.
  • the bearing recess 75 thus has an inner diameter that is slightly larger than the outer diameter of the locking bolt 40, 140th
  • Locking bolt 40 In contrast to those shown in Figures 1 and 2 Locking bolt 40 is the illustrated in Figure 4 Locking bolt 140 designed as a hole nozzle 90 and has at its free end 57, that in the in FIG. 4 shown locking position 41 in the locking recess 38 projects, a central passageway 54.
  • This passageway 54 is coaxial with the longitudinal axis 74 of the locking bolt 140 is arranged.
  • the passageway 54 has a comparatively small flow cross section and goes towards his other end 59 in a likewise designed with cylindrical wall parts Channel section 78 via, which has a larger flow area having.
  • the channel part 78 is in turn under training the support and abutment surface 60 in a recess 92 of the larger channel diameter 61 over, the slightly larger is as the outer diameter 62 in the above Recess 92 received spring 39.
  • This is the Compression spring one end at the support and conditioning stage 60 of Locking bolt 140 and supports the other end the supporting and conditioning stage 76 of the lid or head 31 of the cylinder 21.
  • the locking pin 140 has at its free end 57th a perpendicular to its longitudinal axis 74 arranged Active surface 58 on which attack the fluid pressure medium can to the locking pin 140, starting from the in Figure 4 shown locking position 41 in a Unlock release position, in which he except Engagement with the locking recesses 38.1 to 38.8 is, so a rotation of the spindle 35 in a rotational direction 51 or an opposite direction of rotation 52 is not more blocked.
  • the effective area 58 is much larger Flow cross section of the passage channel 54 in the area the free end 57 of the locking bolt 40, 140th As a result, a secure unlocking of the locking bolt 40, 140 allows.
  • Locking bolt 40, 140 caused by the spring 39 exerted forces in its locking position 41st to be moved. It can in the case of locking bolts 140 located in the associated locking recess 38th located pressure medium through the passage 54 of the Locking bolt 140 through to the relief channel serving channel 55 flow.
  • FIGs 5 and 6 are hydraulic circuit diagrams illustrated in which particularly advantageous Control means and routes are used.
  • the circuit according to the circuit diagram shown in Figure 5 can be advantageous for operation and operation of a locking bolt 40 equipped locking cylinder 20 is used become. It is understood, however, that the from the Wiring diagram according to Figure 5 resulting switching or Control elements also advantageous in connection with the used in Figure 4 locking bolt 140 can be.
  • a particularly advantageous control of the locking cylinder 20 can be achieved with the circuit according to FIG. 5, because this circuit and the control means used there make it possible that the pressure medium first the Locking bodies 42 is supplied to these in their To transfer unlocking position and that then the Pressure medium optionally the first working chamber 33 or the second working chamber 45 is supplied to a movement of the piston 22 in the first direction 28 or in the second To effect direction 27.
  • This can reduce the wear in the Area of the locking bolt 40 and in the area of Locking recesses 38 are minimized and it can not jamming the locking bolts 40, come especially at low switching pressures.
  • the Locking bodies 142 is supplied to these in their Release unlocking position and that at the same time the pressure medium optionally the first working chamber 33 or the second working chamber 45 is supplied to a Movement of the piston 22 in the first direction 28 or in to effect the second direction 27.
  • load-holding lowering brake means 150.1, 150.2 designated load-holding lowering brake valves provided the effect that upon application of the piston 22 on its first side 46 with that in the first chamber 33rd located pressure medium to form a working pressure, the displacement of the piston 22 in a first Direction 28 causes, simultaneously in the second working chamber 45 on the second side 44 of the piston 22 a through the pressure medium located in the second working chamber 45 applied counter-pressure acts, which is smaller than that Working pressure in the first working chamber 33, leaving a uncontrolled advance of the piston 22 in the first Direction 28 is avoided, and vice versa at Actuation of the piston 22 on its second side 44th with that in the second working chamber 45 located Pressure medium to form a working pressure, the a displacement of the piston 22 in a second direction 27th opposite to the first direction 28 causes simultaneously in the first working chamber 33 at the first Side 46 of the piston 22 by a in the first Working chamber 33 located pressure medium exerted Counterpressure acts, which is smaller than the working pressure in the second working chamber 45, leaving an uncontrolled Adva
  • Each load-holding counterbalance valve 150.1, 150.2 has a Inlets 153.1, 153.2, an outlet 154.1, 154.2 and one Control connection 155.1, 155.2 for the pressure medium, wherein the inlet 153.1 of the first load-holding lowering valve 150.1 is fluidly connected to the first working chamber 33 and wherein the inlet 153.2 of the second load-holding lowering valve 150.2 with the second working chamber 45 fluidly connected, and wherein the outlet 154.1 of the first Load-holding lowering brake valve 150.1 with the control connection 155.2 of the second load-holding lowering valve 150.2 fluidly connected and wherein the outlet 154.1 of the second Load-holding lowering brake valve 150.2 with the control connection 155.1 of the first load-holding lowering valve 150.1 fluid-connected, and with the inlet 153.1, 153.2 and the outlet 154.1, 154.2 of the respective load-holding lowering brake valve 150.1, 150.2 each a backpressure blocking agent 156.1, 156.2 fluidly connected, each one Flow of the pressure medium from the outlet 154.1, 154.2 to the inlet
  • each case between the outlet 154.1 of the first load-holding Senkbrems valve 150.1 and the outlet 154.2 of the second Load-holding lowering brake valve 150.2 is at least one remindströmsperrstoff 160, 161 arranged at a Actuation of the outlet 154.1 of the first load-holding Senkbrems valve 150.1 with pressure medium a pressure medium flow to the outlet 154.2 of the second load-holding lowering valve 150.2 prevented and vice versa in a Actuation of the outlet 154.2 of the second load-holding lowering valve 150.2 with pressure medium a pressure medium flow to the outlet 154.1 of the first load-holding Senkbrems valve 150.1 prevents and in both cases a Supply of the pressure medium to the locking body 42, 142nd allows, so that these in their unlocked position can be transferred.
  • the remindströmsperrstoff 160, 161 a first inlet 164 for the pressure medium, a second inlet 165 for the pressure medium and an outlet 166 for the pressure medium, wherein the first inlet 164 of the respective remindströmsperrstoffs 160, 161 with the Outlet 154.1 of the first load-holding lowering valve 150.1 fluidly connected, and wherein the second inlet 165 of the respective remindströmsperrstoffs 160, 161 with the outlet 154.2 of the second load-holding lowering valve 150.2 fluidly connected, and wherein the first inlet 164 of the respective remindströmsperrstoffs 160, 161 and the second Inlet 165 of the respective remindströmsperrstoffs 160, 161st are connected to each other via a fluid channel 167, in the one with the outlet 166 of the respective remindströmsperrstoffs 160, 161 connected fluid channel 167 at a Occluence 168 opens so that from the confluence 168 a first channel part 169 of the fluid channel 167 and a second channel portion 170 of
  • a locking member 171 for shutting off the first channel part 169 or the second channel portion 170 is provided, and wherein in the locked State of the second channel part 170 of the first inlet 164 of the remindströmsperrstoffs 160, the first channel part 169th and the outlet 166 of the non-return valve 160 fluid-connected, so that a pressure medium flow both from the first inlet 164 of remindströmsperrstoffs 160th to the outlet 166 of remindströmsperrstoffs 160 and the Outlet 166 of remindströmsperrstoffs 160 to the first Inlet 164 of the non-return valve 160 is allowed, and vice versa, in the locked state of the first Channel portion 169, the second inlet 165 of the remindströmsperrstoffs 160, the second channel part 170 and the outlet 166 of remindströmsperrstoffs 160 are fluidly connected, so that a pressure medium flow both from the second inlet 165 of the remindströmsperrstoffs 160 to the outlet 166 of remindrffens 160 as well as
  • the respective remindströmsperrstoff 156.1, 156.2 a Blocking member 173.1, 173.2 to prevent a flow of pressure medium from the inlet 153.1, 153.2 to the outlet 154.1, 154.2 of the respective load-holding lowering brake means 150.1, 150.2, which by spring forces of a spring 174.1, 174.2 is applied, so that opening the remindströmsperrstoffs 156.1, 156.2 and thus a pressure medium flow from the outlet 154.1, 154.2 to the inlet 153.1, 153.2 of the respective load-holding lowering brake means 150.1, 150.2 only after exceeding a limit pressure of the Pressure medium is possible, its value of one Spring characteristic of each spring 174.1, 174.2 depends.
  • These springs 174.1 and 174.2 are also good in FIG the lower ends of the two load-holding lowering valves 150.1, 150.2 can be seen.
  • a first locking member 172.1 for shutting off the first Channel part 169 and a second locking member 172.2 to Shut off the second channel part 170 is provided, the first channel part 169 and the second channel part 170 with regard to a flow of pressure medium from the outlet 166 of the Backflow blocking means 161 to the first inlet 164 of the remindströmsperrstoffs 161 and the second inlet 165 of the remindströmsperrstoffs 161 shut off and a pressure fluid flow from the first inlet 164 of the remindströmsperrstoffs 161 to the outlet 166 of remindströmsperrstoffs 161 and from the second inlet 165 of the remindströmsperrstoffs 161 to Allow outlet 166 of the remindströmsperrstoffs 161.
  • the spring 174.1 of the backflow 156.1 depends Pressure medium initially not in the channel 49 and thus not get into the working space 33, but passes first via the first inlet 164 into the first channel part 169 of the as a shuttle valve designed stuntströmsperrffens 160, whereby the blocking means 171 under opening a Flow path via the discharge point 168 in the Fluid channel 167 and from there via the outlet 166 in the Switching channel 47 under substantially simultaneously Closing the second channel part 165 in the in FIG. 5 Locking position shown on the left is moved.
  • the pressure medium then flows through the first then Switching channel 47 to the pressure medium spaces in the region of free ends 57 of the locking bolts 40 and causes that these from the locking position 41 shown in FIG the direction 27 is transferred to its unlocked position become.
  • the sealing surfaces 97 of the locking bolt 40 abut against the mating surfaces 98, it gets lost a further supply of pressure medium in the flow channel 86 there to another pressure rise, which leads that the spring-loaded remindströmsperre 156.1 opens.
  • the pressure medium through the channel 49 in the first Working chamber 49 flow to a movement of the piston 22nd and thus the piston rod 23 in the extension direction 28 too cause.
  • the control takes place in such a way that the here of the Load-holding lowering brake means 150.2 counter-pressure set depending on the movement of the piston 22 along the Cylinder 21 causing working pressure in the flow channel 86 is controlled, with increasing working pressure of the simultaneously acting back pressure decreases, and indeed preferably inversely proportional to the working pressure. In this way, it is always achieved during driving that the piston 22 with one of its current direction of movement opposing force is "clamped", which an uncontrolled advance of the piston 22 prevented becomes.
  • both the Supply passage 86 and the return passage 87 pressure relieved are preferably both the Supply passage 86 and the return passage 87 pressure relieved. This closes both the return valves 156.1 and 156.2 as well - due to the then also in the Control channels 88.1 and 88.2 occurring pressure relief - the two load-holding lowering valves 150.1 and 150.2, so that in the working chambers 33 and 45 located Pressure medium can not escape from it.
  • the piston 22 is so then between the ones on both its sides 44 and 46 clamped existing pressure columns and in its current Fixed stroke position.
  • a pressure relief on the channels 86 and 87 affects also in the switching channel 47 accordingly, so that the Locking bolt 40 by acting on them Spring forces of the springs 39 in the direction 28 of their Entriegelungs ein in the shown in the figures Locking position 41 can be transferred. there This can be in the pressure medium spaces before the free Locking ends 57 of the locking pin 40 located Pressure medium via the channel 47 and the shuttle valve 160th here flow back into the flow channel 86.
  • the flow channel 86 with a pressure medium flow can be applied pressure medium over the connected in parallel with the load-holding lowering brake valve 150.1 remindströmsperre 156.1 in the channel 49 and from there in reach the first working chamber 33 and at the same time over the first check valve 84 of the remindströmsperrstoffs 161st get into the switching channel 47.
  • the pressure medium flows so then via the first inlet 164 of the remindströmsperrstoffs 161 in the first channel part 169 of the fluid channel 159 and there via the estuary 168 in the branched off Fluid channel 167 and again from there into the switching channel 47th
  • the second check valve 85 of the remindströmsperrstoffs 161 closed, d. H. whose locking member 172.2 locks the second channel part 170.
  • the pressure fluid flowing back through the channel 55 can, depending after which of the channels 86 or 87 pressurizes is, either via the check valve 82 or via the check valve 83 in the channel 86 or in the Channel 87 are returned.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Fluid-Damping Devices (AREA)
  • Lock And Its Accessories (AREA)
  • Braking Arrangements (AREA)
  • Chairs Characterized By Structure (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP04025023A 2003-12-04 2004-10-21 Vérin verrouillable Active EP1538343B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL04025023T PL1538343T3 (pl) 2003-12-04 2004-10-21 Cylinder ryglujący

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10356596 2003-12-04
DE10356596A DE10356596B3 (de) 2003-12-04 2003-12-04 Verriegelungszylinder

Publications (3)

Publication Number Publication Date
EP1538343A2 true EP1538343A2 (fr) 2005-06-08
EP1538343A3 EP1538343A3 (fr) 2005-08-10
EP1538343B1 EP1538343B1 (fr) 2007-02-07

Family

ID=34442434

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04025023A Active EP1538343B1 (fr) 2003-12-04 2004-10-21 Vérin verrouillable

Country Status (5)

Country Link
EP (1) EP1538343B1 (fr)
AT (1) ATE353404T1 (fr)
DE (2) DE10356596B3 (fr)
ES (1) ES2282778T3 (fr)
PL (1) PL1538343T3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1803943A2 (fr) 2005-12-29 2007-07-04 Bümach Engineering International B.V. Vérin avec verrouillage de position mécanique en cas d'absence de pression
EP1995471A2 (fr) 2007-05-25 2008-11-26 Neumeister Hydraulik GmbH Cylindre verrouillable à palier fluidique
DE102006030617B4 (de) * 2005-12-29 2009-09-10 Bümach Engineering International B.V. Druckmittelbetriebener Arbeitszylinder mit mechanischer Wegsperrung im drucklosen Zustand

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005016090B4 (de) * 2005-04-08 2007-02-22 Neumeister Hydraulik Gmbh Einfach wirkender Verriegelungszylinder
DE102016119251A1 (de) * 2016-10-10 2018-04-12 Fbr Facondrehteile Gmbh Hydromechanischer Verriegelungszylinder und hydraulisches Steuersystem zu dessen Betätigung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3106532A1 (de) * 1981-02-21 1982-10-21 Dipl.-Ing. Friedrich Tuschka KG, 7770 Überlingen Ventilanordnung zur steuerung eines hydraulischen stellmotors
FR2534985A3 (fr) * 1982-10-23 1984-04-27 Messerschmitt Boelkow Blohm Verin a blocage perfectionne
EP0322503A2 (fr) * 1987-12-29 1989-07-05 Daihatsu Diesel Mfg. Co., Ltd. Appareil à fluide
JPH08303410A (ja) * 1995-04-27 1996-11-19 Hino Motors Ltd 流体圧シリンダ
EP1106841A2 (fr) * 1999-12-07 2001-06-13 Weber-Hydraulik GmbH Actionneur de positionnement linéaire

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3106532A1 (de) * 1981-02-21 1982-10-21 Dipl.-Ing. Friedrich Tuschka KG, 7770 Überlingen Ventilanordnung zur steuerung eines hydraulischen stellmotors
FR2534985A3 (fr) * 1982-10-23 1984-04-27 Messerschmitt Boelkow Blohm Verin a blocage perfectionne
EP0322503A2 (fr) * 1987-12-29 1989-07-05 Daihatsu Diesel Mfg. Co., Ltd. Appareil à fluide
JPH08303410A (ja) * 1995-04-27 1996-11-19 Hino Motors Ltd 流体圧シリンダ
EP1106841A2 (fr) * 1999-12-07 2001-06-13 Weber-Hydraulik GmbH Actionneur de positionnement linéaire

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN Bd. 1997, Nr. 03, 31. März 1997 (1997-03-31) & JP 08 303410 A (HINO MOTORS LTD), 19. November 1996 (1996-11-19) *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1803943A2 (fr) 2005-12-29 2007-07-04 Bümach Engineering International B.V. Vérin avec verrouillage de position mécanique en cas d'absence de pression
EP1803943A3 (fr) * 2005-12-29 2009-04-08 Bümach Engineering International B.V. Vérin avec verrouillage de position mécanique en cas d'absence de pression
DE102006030617B4 (de) * 2005-12-29 2009-09-10 Bümach Engineering International B.V. Druckmittelbetriebener Arbeitszylinder mit mechanischer Wegsperrung im drucklosen Zustand
EP1995471A2 (fr) 2007-05-25 2008-11-26 Neumeister Hydraulik GmbH Cylindre verrouillable à palier fluidique

Also Published As

Publication number Publication date
EP1538343A3 (fr) 2005-08-10
ES2282778T3 (es) 2007-10-16
DE10356596B3 (de) 2005-06-02
PL1538343T3 (pl) 2007-07-31
DE502004002847D1 (de) 2007-03-22
ATE353404T1 (de) 2007-02-15
EP1538343B1 (fr) 2007-02-07

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