EP1538343B1 - Vérin verrouillable - Google Patents

Vérin verrouillable Download PDF

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Publication number
EP1538343B1
EP1538343B1 EP04025023A EP04025023A EP1538343B1 EP 1538343 B1 EP1538343 B1 EP 1538343B1 EP 04025023 A EP04025023 A EP 04025023A EP 04025023 A EP04025023 A EP 04025023A EP 1538343 B1 EP1538343 B1 EP 1538343B1
Authority
EP
European Patent Office
Prior art keywords
load
outlet
pressure medium
piston
inlet
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.)
Expired - Lifetime
Application number
EP04025023A
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German (de)
English (en)
Other versions
EP1538343A2 (fr
EP1538343A3 (fr
Inventor
Walter Neumeister
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Neumeister Hydraulik GmbH
Original Assignee
Neumeister Hydraulik GmbH
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Publication date
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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
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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 which is movable by means of a fluid pressure medium parallel to the longitudinal axis of the cylinder, and which is provided with a piston thread which engages to form a non-self-locking thread with a spindle thread of a spindle which is rotatable about a rotational axis arranged parallel to the longitudinal axis of the cylinder and which has at least one outwardly open locking recess into which at least one locking body acted upon by spring force of a spring can engage, which is secured against rotation about the axis of rotation of the spindle and movable relative to the cylinder is mounted and which is translatable by means of the spring force of the spring in a locking position in which it engages in the locking recess of the spindle, so that then rotation of the spindle is blocked about its axis of rotation, and wherein the locking body using a it is fluid working against the spring force of the spring from the locking position into an unlocking position
  • Such a locking cylinder has become known from JP 083 034 10 A.
  • a large-volume locking piston through the central passage opening, a shaft of a ball screw extends and which is integrally connected to a plurality of concentric with the spindle and arranged upstanding along the spindle teeth.
  • the teeth of the locking piston are in engagement with opposite teeth of a gear which is rotatably connected to this concentric receiving spindle.
  • the locking piston has on its side facing away from the teeth side a hollow portion with an internal toothing, and the tooth flanks of the teeth of the internal toothing extend parallel to the axis of rotation of the spindle.
  • the internal gear is engaged with a matching external toothing of a pinion, which is fixedly connected to a cover plate of the cylinder.
  • the locking piston is displaceable parallel to the axis of rotation of the ball screw, but stored blocked against rotation about the spindle axis.
  • a circumferential seal is provided which seals a pressure medium acted upon pressure medium space to the end cap of the cylinder.
  • This construction of a locking unit is complicated and takes up comparatively much space.
  • For unlocking or locking the design-related large and compact and therefore important locking piston comparatively large forces are needed and / or it must comparatively long locking or locking times are accepted, which also means a corresponding security risk.
  • the locking piston must be sealed at its outer periphery with a circumferential seal, which leads to corresponding frictional forces when moving the locking piston for the purpose of locking or unlocking, whereby the efficiency of this locking cylinder is limited.
  • the ball screw is clamped to the cylinder via a ball bearing and arranged at the free end of the spindle shaft slide bearing clamped that a movement of the spindle in the longitudinal direction of the cylinder is not possible, while a rotation of the spindle about its longitudinal axis is possible.
  • the free end of the spindle shaft slidably supported on an inner surface of the end cap of the cylinder and the ball bearing is fixed by means of a screwed onto an external thread of the ball screw nut against a transverse to the cylinder paragraph.
  • This design is limited to applications where only relatively small loads can be lifted. For larger loads, however, it can lead to wear up to the feeding of the plain bearing. This can lead to the formation and detachment of metal chips or particles, which may affect the function of the locking unit, up to a blockade of the locking piston. This means an unacceptable security risk.
  • the control of the locking piston having the locking unit and the control of the movement of the piston take place in this construction via mechanically coupled directional control valves such that it can come in the raising or lowering of the load to an undesirable advance of the piston.
  • cavitation may occur at the piston seal and the piston rod, which means a safety risk and correspondingly limits the service life.
  • the locking cylinder comprises a cylinder and a piston, which uses one of two sides of the piston in a first working chamber and fluid pressure means feedable into a second working chamber is movable parallel to the longitudinal axis of the cylinder and provided with a piston thread engaging a spindle thread of a spindle forming a parallel thread to a longitudinal axis of the spindle to form a non - self - locking thread
  • Cylinder arranged axis of rotation is rotatable and which has at least one outwardly open locking recess into which at least one acted upon by spring force of a spring locking body can be secured against rotation about the axis of rotation of the spindle and fixedly connected to the cylinder, but relative to this movable is mounted, and which is transferred by means of the spring force of the spring in a locking position in which it engages in the locking recess of the spindle, so that then rotation of the spindle is blocked about its axis of rotation, and wherein the locking body using a
  • a locking cylinder can be provided, which allows for increased application and possible applications and longer life a higher reliability.
  • the counterpressure controlled by the load-holding lowering brake means is controlled in dependence on the respective working pressure causing the piston to move along the cylinder so that the simultaneously acting back pressure decreases with increasing working pressure.
  • the backpressure is controlled inversely proportional to the working pressure.
  • the load-holding lowering brake means each have a first inlet for the pressure medium, an outlet for the pressure medium and a control port for the pressure medium, wherein the inlet of the first load-holding Senkbrems means with the first working chamber fluidly connected and the inlet of the second load-holding lowering brake fluid is fluidly connected to the second working chamber, and wherein the outlet of the first load-holding Senkbrems agent is fluidly connected to the control port of the second load-holding Senkbrems means and the outlet of the second load-holding Senkbrems -Mittel with the control terminal the first load-holding lowering brake fluid is fluidly connected, and wherein each of the inlet and the outlet of the respective load-holding lowering brake fluid communication is a remindströmsperrstoff, each having a flow of the pressure medium from the outlet to the inlet of the respective load-holding lowering brake means allows, but blocks an opposite direction, and that either the outlet of the first load-holding lowering brake means and thus the control terminal
  • Control connection of the first load-holding lowering brake means are acted upon with pressure medium to a movement of the piston in the first direction or in the second direction due to the respective working pressure and with simultaneous formation of the respective back pressure, via the second load-holding Senkbrems-means or via the first load-holding lowering brake means depending on the pressure acting on the respective control port pressure to effect.
  • either 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 application of the outlet of the first Load-holding lowering brake means or the outlet of the second load-holding Senkbrems means with pressure medium, this is supplied to the locking body or the locking bodies to convert this or this in his or her unlocked position.
  • At least one remindströmsperrstoff is arranged, which upon application of the outlet of the first load-holding Senkbrems means with pressure medium prevents pressure fluid flow to the outlet of the second load-holding Senkbrems agent and vice versa upon application of pressure to the outlet of the second load-holding Senkbrems means prevents pressure fluid flow to the outlet of the first load-holding Senkbrems agent, and in both cases a Supply of the pressure medium to the locking body or the locking bodies permits, so that this or this is transferred to its unlocking position or will be.
  • the non-return valve comprises a first inlet for the pressure medium, a second inlet for the pressure medium and an outlet for the pressure medium, wherein the first inlet of the remindströmsperrstoffs is fluidly connected to the outlet of the first load-holding lowering brake means and wherein the second inlet of the non-return valve is in fluid communication with the outlet of the second load-holding counter-brake fluid, and wherein the first inlet of the non-return valve and the second inlet of the non-return valve are interconnected via a fluid passage into which one connected to the outlet of the non-return valve Fluid channel opens at an orifice, so that branches off from the discharge point, a first channel part of the fluid channel and a second channel part of the fluid channel, 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 passage member, the first inlet of the remindströmsperrstoffs, the first channel part and the outlet of
  • the non-return valve comprises a first inlet for the pressure medium, a second inlet for the pressure medium and an outlet for the pressure medium, wherein the first inlet of the remindströmsperrschs is fluidly connected to the outlet of the first load-holding lowering brake means and wherein the second inlet of the non-return valve is in fluid communication with the outlet of the second load-holding counter-brake fluid, and wherein the first inlet of the non-return valve and the second inlet of the non-return valve are interconnected via a fluid passage into which one connected to the outlet of the non-return valve Fluid channel opens at an orifice, so that branches off from the orifice a first channel part of the fluid channel and a second channel part of the fluid channel, and wherein a first locking member for shutting off the the first channel part and a second locking member for shutting off the second channel part is provided, which shut off the first channel part and the second channel part in terms of a pressure fluid flow from the outlet of the
  • the working means or the pressure means is supplied to the locking body or the locking bodies in order to transfer this or these in its unlocking position and that at the same time the pressure medium selectively supplied to the first working chamber or the second working chamber is to cause movement of the piston in the first direction or in the second direction.
  • the working means or the pressure means is first supplied to the locking body or the locking bodies in order to transfer this or these in his or her unlocking position and then that the pressure medium optionally the first working chamber or the second working chamber is supplied to cause movement of the piston in the first direction or in the second direction.
  • the respective backflow blocking means A blocking member for preventing a flow of pressure medium from the inlet to the outlet of the respective load-holding lowering brake means, which is acted upon by spring forces of a spring, so that an opening of the remindströmsperrstoffs and thus a pressure medium flow from the outlet to the inlet of the respective load-holding Senkbrems- Means is only possible from above a limit pressure of the pressure medium, the value of which depends on a spring characteristic of the respective spring.
  • 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 extends from its end face 44 coaxial with the cylinder longitudinal axis 29.
  • 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 base 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 mountainsbrooke trapezoidal coarse thread, which 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 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 is sealed relative to the second working chamber 33 via the annular seal 68 of the piston 22.
  • a flange-shaped projection 65 In the area of the free end 67 of the spindle 35 facing away end 77 of the spindle 35, this is rotatably connected to a flange-shaped projection 65. This has a transversely in the region of its cylinder bottom end or at right angles to the axis of rotation 43 of the spindle 35 extending, here annular wall portion 79. This is mounted on the free end 67 of the spindle 35 side facing by a first thrust bearing 120, here in the form of a first ring bearing 127, which is designed here as a needle bearing 138, at a support and investment level of the cylinder extension 66. This designed as a rolling bearing 137 ring bearing 127 serves to absorb the force acting on the spindle 35 in the extension direction 28 axial forces. In order to be able to absorb the axial forces acting on the spindle 35 in the retraction direction 27 in the opposite direction to the extension direction 28, two measures are taken:
  • a second thrust bearing 121 is provided in the form of a second annular bearing 130 arranged at the head end 77 of the spindle 35.
  • This thrust bearing 121 is also designed as a roller bearing 122 in the form of a needle bearing 123. It is on a coaxial with the axis of rotation 43 of the spindle 35 fixedly connected to the spindle 35 supporting body 124 received in the form of a cylinder pin 125 which extends in the direction of the cylinder bottom or head 31 of the cylinder 21 and the coaxial with the axis of rotation 43 spindle 35 is arranged ,
  • a disc spring package 135, Adjoining the needle bearing 123 in the retraction direction 27 is a disc spring package 135, which consists of a plurality of disc springs 134, 136. In the embodiment shown, five disc springs 134 and five disc springs 136 are provided. In this case, the disc springs 134 and the disc springs 136th each alternately successively preferably arranged such that in each case the spring travel of each plate spring 134, 136 for a resilient mounting of the spindle 35 is available.
  • 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 resulting forces are absorbed, that is 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 portion 79 with here a total of eight locking recesses 38.1 to 38.8, which are open to the cylinder bottom 53 out to the outside.
  • the locking recesses 38.1 to 38.8 are arranged at equal angular distances from each other on an imaginary circumferential circle such that two locking recesses are arranged diametrically opposite one another and are therefore arranged on a line containing the axis of rotation 43 of the spindle 35.
  • Each locking recess 38 is configured with conically inwardly tapering wall portions 70 and serves to receive outwardly conically tapered wall portions 72 of locking bolts 40, 140.
  • the tapered wall portions 72 having free end 57 of the respective locking bolt 40, 150 is preferably designed in such a manner on 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 can be brought into fluid communication with channels 48 and 49, via which the piston 22 can be acted upon by pressure medium on its respective sides 44 and 46.
  • FIG. 1 A first embodiment of a Verriegelungsbolzens.40 is shown in Figures 1 and 2 and a second embodiment of a locking bolt 140 is illustrated in Figure 4.
  • the locking bolt 40 is designed to be cross-sectionally closed in the region of its free end 57, while the locking bolt 140 is provided as a perforated nozzle 90 with a through-channel 54 which is open towards its free end 57 and concentric with its longitudinal axis 74. Except for this passage 54, however, the locking bolts 40 and 140 are identical, wherein like reference numerals refer to like elements.
  • Each locking bolt 40, 140 is designed as a preferably elongated cylinder pin 69 rotationally symmetrical to its longitudinal axis 74.
  • Each locking bolt 40, 140 has a circular cylindrical outer contour 50 and a circular cylindrical inner contour, is thus designed as a rotary hollow body.
  • Each locking bolt 40, 140 also has a circular cylindrical recess 92 which is formed with parallel to the longitudinal axis 74 of the respective locking bolt 40, 140 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. This is received in the mounted state with a spring portion 93 in the recess 92.
  • 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 from.
  • a radially outwardly extending abutment and counter-sealing surface 98 for the locking pin 40, 140 is provided, which is arranged perpendicular to the wall portions bounding the bearing recess 75 ,
  • Each locking bolt 40, 140 has at its head or spring-side end 59 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, 140 has.
  • This ring-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, 140 has been transferred into its unlocked position after being subjected to the pressing forces exerted by the pressure medium in unlocking 27 , 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, 140 occurs.
  • the abutment and Abdichtitch configuration 96 advantageously limits the respective Entriegelungshub the locking pins 40, 140th
  • Each locking bolt 40, 140 is slidably mounted parallel to the axis of rotation 43 of the spindle 35 with little clearance in the bore or bearing recess 75 having a cylindrical inner contour 98, that is, starting from the locking position 41 shown in FIGS. 1, 2 and 4. or unlocking direction 27 using the pressure medium 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, 140 return spring forces be transferred back to 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, 140.
  • the locking bolt 140 illustrated in FIG. 4 is configured as a hole nozzle 90 and has a free end 57 which protrudes into the locking recess 38 in the locking position 41 shown in FIG central passageway 54.
  • This through-passage 54 is arranged coaxially with the longitudinal axis 74 of the locking bolt 140.
  • the through-passage 54 has a comparatively small through-flow cross-section and, in the direction of its other end 59, merges into a likewise with cylindrical wall parts designed channel part 78, which has a larger flow area.
  • the channel part 78 in turn, forming the support and contact surface 60 in a recess 92 of the larger channel diameter 61, which is slightly larger than the outer diameter 62 of the spring 39 received in said recess 92.
  • the compression spring is at one end to the support And investment level 60 of the locking bolt 140 and is supported at the other end of the support and investment stage 76 of the lid or head 31 of the cylinder 21 from.
  • the locking bolt 140 has at its free end 57 a perpendicular to its longitudinal axis 74 arranged active surface 58 to which the fluid pressure medium can act to transfer the locking bolt 140, starting from the locking position 41 shown in Figure 4 in an unlocking position, in which he out of engagement with the locking recesses 38.1 to 38.8, so no rotation of the spindle 35 in a rotational direction 51 or an opposite direction of rotation 52 is no longer blocked.
  • the active surface 58 is much larger than the flow cross-section of the through-channel 54 in the region of the free end 57 of the locking bolt 40, 140. This enables a secure unlocking of the locking bolt 40, 140.
  • the locking bolt 40, 140 can be at a pressure relief in the locking recesses 38, it is intended, for the purpose of fixing the piston 22 with its piston rod 23 in a certain stroke position, or be it unintentionally, for example in the event of leakage or a total failure of the hydraulic system, the locking bolt 40, 140 are moved due to the forces exerted by the spring 39 forces in its locking position 41.
  • the pressure medium located in the associated locking recess 38 can flow through the through-passage 54 of the locking bolt 140 into the channel 55 serving as the relief channel.
  • a particularly advantageous control of the locking cylinder 20 can be achieved with the circuit of Figure 5, because this circuit and the control means used there make it possible that the pressure medium is first supplied to the locking bodies 42 in order to convert them into their unlocked position and then the pressure medium either the first working chamber 33 or the second working chamber 45 is supplied to cause a movement of the piston 22 in the first direction 28 or in the second direction 27.
  • the wear in the area of the locking bolts 40 and in the area of the locking recesses 38 can be minimized and the locking bolts 40 can not become jammed, in particular at low switching pressures.
  • the working medium or the pressure medium is supplied to the locking bodies 142 in order to place them in their position Unlock unlocking position and that at the same time the pressure medium is optionally the first working chamber 33 or the second working chamber 45 is supplied to cause a movement of the piston 22 in the first direction 28 or in the second direction 27.
  • load-holding Senkbrems means 150.1, 150.2 load holding Senkbrems valves are provided which cause when pressurizing the piston 22 on its first side 46 with the in the first chamber 33 pressure medium to form a working pressure, the causing a displacement of the piston 22 in a first direction 28, at the same time in the second working chamber 45 on the second side 44 of the piston 22, a counter pressure exerted by the pressure medium in the second working chamber 45 acts, which is smaller than the working pressure in the first working chamber 33, so that an uncontrolled advance of the piston 22 in the first direction 28 is avoided, and that conversely upon application of the piston 22 on its second side 44 with the pressure medium in the second working chamber 45 to form a working pressure, the displacement of the piston 22 in a second direction 27 opposite to the first direction 28 causes, at the same time in the first working chamber 33 on the first side 46 of the piston 22, a pressure exerted by the pressure medium in the first working chamber 33 acts counterpressure, which is smaller than the working pressure in the second working chamber 45, so
  • Each load-holding lowering brake valve 150.1, 150.2 has an inlet 153.1, 153.2, an outlet 154.1, 154.2 and a control connection 155.1, 155.2 for the pressure medium, wherein the inlet 153.1 of the first load-holding lowering valve 150.1 fluidly connected to the first working chamber 33 and wherein the inlet 153.2 of the second load-holding lowering valve 150.2 is fluidly connected to the second working chamber 45, and wherein the outlet 154.1 of the first load-holding lowering valve 150.1 is fluidically connected to the control port 155.2 of the second load-holding lowering valve 150.2 and wherein the outlet 154.1 of the second load-holding lowering brake valve 150.2 is fluidically connected to the control port 155.1 of the first load-holding lowering valve 150.1, and wherein with the inlet 153.1, 153.2 and the outlet 154.1, 154.2 of the respective load-holding lowering valve 150.1, 150.2 each a backpressure blocking means 156.1, 156.2 is fluidly connected, each having a flow of the pressure medium of the Outlet 154.1, 154.2 to the inlet
  • At least one remindströmsperrstoff 160, 161 is arranged, which upon exposure of the outlet 154.1 of the first load-holding Senkbrems valve 150.1 with Pressure medium prevents a pressure fluid flow to the outlet 154.2 of the second load-holding lowering valve 150.2 out and vice versa upon application of the outlet 154.2 of the second load-holding lowering valve 150.2 with pressure medium, a pressure fluid flow to the outlet 154.1 of the first load-holding Senkbrems valve 150.1 out prevented and that in both cases allows a supply of the pressure medium to the locking body 42, 142, so that they can be transferred to their unlocked position.
  • the non-return valve means 160, 161 has 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 fluidly connected to the outlet 154.1 of the first load-holding Senkbrems valve 150.1, and wherein the second inlet 165 of the respective remindströmsperrstoffs 160, 161 fluidly connected to the outlet 154.2 of the second load-holding Senkbrems valve 150.2, and wherein the first inlet 164 of the respective remindströmsperrstoffs 160, 161 and the second inlet 165 of the respective remindströmsperrstoffs 160, 161 are interconnected via a fluid passage 167, in which a connected to the outlet 166 of the respective remindströmsperrstoffs 160, 161 fluid channel 167 at an orifice 168th opens, so that a first channel portion 169 of the fluid channel 167 and a second channel portion 170 of the fluid
  • a blocking element 171 is furthermore provided for shutting off the first channel part 169 or the second channel part 170, and in the shut-off state of the second channel part 170 the first inlet 164 of the non-return means 160, the first channel part 169 and the outlet 166 of FIG Backflow blocking means 160 are fluidly connected, so that a pressure medium flow from both the first inlet 164 of the remindströmsperrstoff 160 to the outlet 166 of remindströmsperrstoff 160 and the outlet 166 of the remindströmsperrstoff 160 to the first inlet 164 of the scaffoldströmsperrstoff 160 is allowed, and vice versa, in the locked state of the first Portion 169, the second inlet 165 of the remindströmsperrstoffs 160, the second channel portion 170 and the outlet 166 of the remindströmsperrstoffs 160 fluidly connected, so that a pressure fluid flow from both the second inlet 165 of the remindströmsperrstoff 160 to the outlet 166 of remindrffens 160 as well as the inlet 164
  • the respective nonreturn blocking means 156.1, 156.2 has a blocking member 173.1, 173.2 for preventing a pressure medium flow 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 is acted upon by spring forces of a spring 174.1, 174.2, so that an opening of the remindströmsperrstoffs 156.1, 156.2 and consequently a flow of pressure medium 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 from above Limit pressure of the pressure medium is possible, the value of a spring characteristic of the respective spring 174.1, 174.2 depends.
  • These springs 174.1 and 174.2 are also well visible in Figure 1 at the lower ends of the two load-holding lowering valves 150.1, 150.2 there.
  • a first blocking element 172.1 is provided for shutting off the first channel part 169 and a second blocking element 172.2 is provided for shutting off the second channel part 170 which comprises the first channel part 169 and the first channel part 169 second passage portion 170 with respect to a flow of pressurized fluid from the outlet 166 of the remindströmsperrstoffs 161 to the first inlet 164 of the remindströmsperrstoffs 161 and the second inlet 165 of the remindströmsperrstoffs 161 shut off and the one Druckstoffströmung 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 the outlet 166 of the remindströmsperrstoffs 161.
  • the load-holding lowering brake valves 150.1 and 150.2 thus already make it possible to secure the respective stroke position of the piston 22 with the piston rod 23 relative to the cylinder 21, both when using the locking cylinder 20 for the transmission of compressive forces and for the transmission of tensile forces ,
  • the channel designated here with feed channel 86 is subjected to pressure medium, ie. H. it is supplied by means of a pump not shown in the figures through the flow channel 86, the pressure medium.
  • the pressure medium can not initially enter the channel 49 and thus not in the working space 33, but first passes through the first inlet 164 in the first channel part 169 of as a shuttle valve designed stuntströmsperrstoffs 160, whereby its blocking means 171 is moved into the fluid channel 167 via the outlet point 166 and from there via the outlet 166 into the switching channel 47 with substantially simultaneous closing of the second channel part 165 into the blocking position shown on the left in FIG. 5, opening a flow path.
  • the channel 88.1 leading to the control connection 155 of the second load-holding lowering brake valve 150.2 is subjected to pressure medium.
  • the pending pressure medium pressure still causes no opening of the second load-holding lowering valve 150.2.
  • the respective load-holding lowering brake means 150.1 and 150.2 opens only from a certain, prevailing at the respective control port 155.1 or 155.2 pressure medium pressure, depending on the set on the springs 80.1 and 80.2 spring forces or spring characteristics.
  • the pressure medium then flows first through the switching channel 47 to the pressure medium spaces in the region of the free ends 57 of the locking bolt 40 and causes them to be transferred from the locking position 41 shown in the direction 27 in its unlocked position become.
  • a further supply of pressure medium into the flow channel 86 causes a further increase in pressure, which causes the spring-loaded backflow barrier 156.1 to open.
  • the pressure medium can flow via the channel 49 into the first working chamber 49 in order to effect a movement of the piston 22 and thus of the piston rod 23 in the extension direction 28.
  • the control takes place in such a way that the counterpressure set here by the load-holding lowering brake means 150.2 is controlled in the supply channel 86 as a function of the working pressure in the supply channel 86 causing the piston 22 to move along the cylinder 21, the counterpressure acting simultaneously decreasing as the working pressure increases, and preferably inversely proportional to the working pressure. In this way, it is always achieved during driving that the piston 22 is "clamped” in a force acting counter to its current direction of movement, thereby preventing an uncontrolled advance of the piston 22.
  • both the flow channel 86 and the return channel 87 are pressure-relieved.
  • both the two return valves 156.1 and 156.2 as well as - due to the pressure relief then occurring in the control channels 88.1 and 88.2 - close the two load-holding lowering valves 150.1 and 150.2 so that the pressure medium located in the working chambers 33 and 45 does not escape therefrom can.
  • the piston 22 is then clamped between the pressure columns present on its two sides 44 and 46 and fixed in its current stroke position.
  • a pressure relief at the channels 86 and 87 also has an effect in the switching channel 47, so that the locking bolts 40 can be transferred from their unlocking position into the locking position 41 shown in the figures by the spring forces of the springs 39 acting on them ,
  • the located in the pressure medium spaces in front of the free locking ends 57 of the locking bolt 40 pressure fluid via the channel 47 and the shuttle valve 160 here flow back into the flow channel 86.
  • the locking bolts 40 then engage either in the locking recesses 38 or are these at the head 31 of the cylinder 21 indicative end face of the locking recesses 38 containing ring lug 65, which is located between two immediately adjacent Locking recesses 38 are located.
  • any holding stroke position of the piston 22 it is not relevant in the normal case, whether the locking pin 40 or 140 engage in the locking recesses 38.
  • the approach containing the locking recesses 38 still continues to rotate slightly until the locking pins 40, 140 engage in the next-reaching locking recess 38. In the embodiments shown and described, however, it can only come to a very small stroke of the piston 22, which is in the millimeter range and which is completely sufficient in terms of safety.
  • the mode of operation and function of the load-holding lowering brake means 150.1, 150.2 is the same as explained with reference to the example of the circuit according to FIG. 5, so that reference may be made to the above description parts.
  • the flow channel 86 is acted upon by a pressure medium flow, pressure medium via the parallel to the load-holding Senkbrems valve 150.1 switched backflow 156.1 into the channel 49 and from there into the first working chamber 33 and can at the same time via the first check valve 84 of the remindströmsperrstoffs 161 get into the switching channel 47.
  • the pressure medium then flows via the first inlet 164 of the remindströmsperrstoffs 161 in the first channel portion 169 of the fluid channel 159 and from there via the discharge point 168 in the branched fluid channel 167 and again from there into the switching channel 47.
  • the second check valve 85 of the remindströmsperrstoffs 161 closed, ie their locking member 172.2 blocks the second channel part 170th
  • the piston 22 can move in the extension direction 28 due to a simultaneous application of pressure medium on its side facing the cylinder bottom 53.
  • both the two backflow shutters 156.1 and 156.2 and both load hold lowering brake valves 150.1 and 150.2 close.
  • the locking bolts 140 are displaced by the springs 39 in the extension direction 28, so that they can latch 38 depending on the current position of the locking recesses 38, so that locked in the locking position 41, the spindle 35 and thus the piston 22 both hydraulically and mechanically are.
  • the return passage 87 can be acted upon with pressure medium, that is, the pressure medium can be supplied there.
  • the pressure medium can then pass through the check valve 156.2 in the channel 48 and from there into the working chamber 45, so that the side facing the piston rod end side 44 of the piston 42 can be acted upon with pressure medium.
  • a branched-off pressure medium flow from the return passage 87 via the second check valve 85 of the return flow blocking means 161 again reaches the switching passage 47, while the first check valve 84 is closed.
  • the pressure medium flowing back through the channel 55 can be returned to the channel 86 or the channel 87 either via the check valve 82 or via the check valve 83, depending on which of the channels 86 or 87 is pressurized.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Lock And Its Accessories (AREA)
  • Fluid-Damping Devices (AREA)
  • Braking Arrangements (AREA)
  • Chairs Characterized By Structure (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Claims (11)

  1. Vérin de verrouillage (20) avec un vérin (21) et un piston (22) qui est déplaçable à l'aide d'un milieu de pression fluide pouvant être amené aux deux côtés du piston (22) dans une première chambre de travail (33) et une seconde chambre de travail (45) parallèlement à l'axe longitudinal (29) du vérin (21), et qui présente un taraudage de piston (34) qui, en réalisant un taraudage non auto-bloquant (37), est en prise avec un filetage (36) d'une broche (35) qui peut tourner autour d'un axe de rotation (43) disposé parallèlement à l'axe longitudinal (29) du vérin (21) et qui présente au moins un évidement de verrouillage (38) ouvert vers l'extérieur dans lequel peut s'engager au moins un corps de verrouillage (42, 142) sollicité au moyen de la force d'un ressort, qui est assuré à l'encontre d'une rotation autour de l'axe de rotation (43) de la broche (35) et qui est relié fixement au vérin (21), cependant est logé d'une manière mobile relativement à celui-ci, et qui peut être amené à l'aide de la force du ressort (39) dans une position de verrouillage (41) dans laquelle il s'engage dans l'évidement de verrouillage (38) de la broche (35) de sorte qu'une rotation de la broche (35) autour de son axe de rotation (43) est bloquée, et où le corps de verrouillage (42, 142) peut être amené à l'aide d'un agent de travail fluide contre la force du ressort (35) de la position de verrouillage (41) dans une position de déverrouillage dans laquelle la broche (35) peut tourner autour de son axe de rotation (43) pour permettre un déplacement du piston (22) le long du vérin (21), et où sont prévus des moyens de commande pour commander le mouvement du piston (22) et du corps de verrouillage (42, 142) respectivement des corps de verrouillage (42, 142), où au moins un premier moyen de maintien de charge - descente freinée (150.1) est relié fluidement avec la première chambre de travail (33) et en ce qu'au moins un second moyen de maintien de charge - descente freinée (150.2) est relié fluidement avec la seconde chambre de travail (45), où les au moins deux moyens de maintien de charge - descente freinée (150.1, 150.2) font que lors de la sollicitation du piston (22) sur son premier côté (46) par le milieu de pression se trouvant dans la première chambre de travail (33), en réalisant une pression de travail qui entraîne un déplacement du piston (22) dans une première direction (28), il règne en même temps dans la seconde chambre de travail (45) au second côté (44) du piston (22) une contre-pression exercée par le milieu de pression se trouvant dans la seconde chambre de travail (45), qui est plus petite que la pression de travail dans la première chambre de travail (33) de sorte qu'une avance non contrôlée du piston (22) dans la première direction (28) est évitée, et en ce que, inversement, lors de la sollicitation du piston (22) sur son second côté (44) avec le milieu de pression se trouvant dans la seconde chambre de travail (45), en réalisant une pression de travail qui provoque un déplacement du piston (22) dans une seconde direction (27) opposée à la première direction (28), il règne en même temps dans la première chambre de travail (33) au premier côté (46) du piston (22) une contre-pression exercée par le milieu de pression se trouvant dans la première chambre de travail (33), qui est plus petite que la pression de travail dans la seconde chambre de travail (45), de sorte qu'une avance non contrôlée du piston (22) dans la seconde direction (27) est évitée, et où les moyens de maintien de charge - descente freinée (150.1, 150.2), lors d'une détente de pression souhaitée, dans le but de maintenir le piston (22) dans une position de course souhaitée, arrête un reflux du milieu de pression des deux chambres de travail (33, 45) de sorte que le piston (22) est maintenu par le milieu de pression se trouvant dans les chambres de travail (35, 45) dans la position de course souhaitée, caractérisé en ce que la contre-pression commandée par les moyens de maintien de charge - descente freinée (150.1, 150.2) est commandée en fonction de la pression de travail respective, provoquant un déplacement du piston (22) le long du vérin (21).
  2. Vérin de verrouillage selon la revendication 1, caractérisé en ce que la contre-pression commandée par les moyens de maintien de charge - descente freinée (150.1, 150.2) est commandée en fonction de la pression de travail respective, provoquant un déplacement du piston (22) le long du vérin (21), de sorte que lors d'une pression de travail croissante, la contre-pression agissant en même temps diminue.
  3. Vérin de verrouillage selon la revendication 2, caractérisé en ce que la contre-pression est commandée d'une manière inversement proportionnelle à la pression de travail.
  4. Vérin de verrouillage selon l'une des revendications 1 à 3, caractérisé en ce que les moyens de maintien de charge - descente freinée (150.1, 150.2) présentent chacun une première entrée pour le milieu de pression (153.1, 153.2), une sortie (154.1, 154.2) pour le milieu de pression et une connexion de commande (155.1, 155.2) pour le milieu de pression, où l'entrée (153.1) du premier moyen de maintien de charge - descente freinée (150.1) est reliée fluidement avec la première chambre de travail (33), et en ce que l'entrée (153.2) du second moyen de maintien de charge - descente freinée (150.2) est reliée fluidement avec la seconde chambre de travail (45), et où la sortie (154.1) du premier moyen de maintien de charge - descente freinée (150.1) est reliée fluidement avec la connexion de commande (155.2) du second moyen de maintien de charge - descente freinée (150.2), et la sortie (154.2) du second moyen de maintien de charge - descente freinée (150.2) est reliée fluidement avec la connexion de commande (155.1) du premier moyen de maintien de charge - descente freinée (150.1), et où est relié à l'entrée (153.1, 153.2) et à la sortie (154.1, 154.2) du moyen de maintien de charge - descente freinée respectif (150.1, 150.2) à chaque fois un moyen d'arrêt de reflux (156.1, 156.2), qui permet à chaque fois un écoulement du milieu de pression de la sortie (154.1, 154.2) à l'entrée (153.1, 153.2) du moyen de maintien de charge - descente freinée respectif (150.1, 150.2), qui bloque cependant à chaque fois dans une direction opposée, et en ce que sélectivement la sortie (154.1) du premier moyen de maintien de charge - descente freinée (150.1) et donc la connexion de commande (155.2) du second moyen de maintien de charge - descente freinée (150.2) ou la sortie (154.2) du second moyen de maintien de charge - descente freinée (150.2) et donc la connexion de commande (155.1) du premier moyen de maintien de charge - descente freinée (150.1) peuvent être chargées en milieu de pression pour provoquer un déplacement du piston (22) dans la première direction (28) ou dans la seconde direction (27) sur la base de la pression de travail respective et sous la réalisation simultanée de la contre-pression respective qui par le second moyen de maintien de charge - descente freinée (150.2) respectivement par le premier moyen de maintien de charge - descente freinée (150.1) en fonction de la pression agissant à la connexion de commande respective (155.1, 155.2).
  5. Vérin de verrouillage selon la revendication 4, caractérisé en ce que sélectivement la sortie (154.1) du premier moyen de maintien de charge - descente freinée (150.1) ou la sortie (154.2) du second moyen de maintien de charge - descente freinée (150.2) sont en liaison fluidique avec le corps de verrouillage (42, 142) respectivement les corps de verrouillage (42, 142) de sorte que lors d'une sollicitation de la sortie (154.1) du premier moyen de maintien de charge - descente freinée (150.1) ou de la sortie (154.2) du second moyen de maintien de charge - descente freinée (150.2) en milieu de pression, celui-ci est amené au corps de verrouillage 42, 142 respectivement aux corps de verrouillage (42, 142) pour amener celui-ci respectivement ceux-ci dans sa respectivement leur position de déverrouillage.
  6. Vérin de verrouillage selon la revendication 4 ou 5, caractérisé en ce qu'il est disposé entre la sortie (154.1) du premier moyen de maintien de charge - descente freinée (150.1) et la sortie (154.2) du second moyen de maintien de charge - descente freinée (150.2) au moyen un moyen d'arrêt de reflux (160, 161) qui, lors d'une sollicitation de la sortie (154.1) du premier moyen de maintien de charge - descente freinée (150.1) en milieu de pression, empêche un écoulement du milieu de pression vers la sortie (154.2) du second moyen de maintien de charge - descente freinée (150.2) et qui, inversement, lors d'une sollicitation de la sortie (154.2) du second moyen du maintien de charge - descente freinée (150.2) en milieu de pression, empêche un écoulement du milieu de pression vers la sortie (154.1) du premier moyen du maintien de charge - descente freinée (150.1), et qui permet dans les deux cas une amenée du milieu de pression au corps de verrouillage respectivement aux corps de verrouillage (42, 142) de sorte que celui-ci respectivement ceux-ci est respectivement sont amenés dans sa respectivement leur position de verrouillage.
  7. Vérin de verrouillage selon la revendication 6, caractérisé en ce que le moyen d'arrêt de reflux (160) présente une première entrée (164) pour le milieu de pression, une seconde entrée (165) pour le milieu de pression et une sortie (166) pour le milieu de pression, où la première entrée (164) du moyen d'arrêt de reflux (160) est reliée fluidement à la sortie (154.1) du premier moyen de maintien de charge - descente freinée (150.1), et où la seconde entrée (165) du moyen d'arrêt de reflux (160) est reliée fluidement à la sortie (154.2) du second moyen de maintien de charge - descente freinée (150.2), et où la première entrée (164) du moyen d'arrêt de reflux (160) et la seconde entrée (165) du moyen d'arrêt de reflux (160) sont reliées entre elles par un canal de fluide (167) dans lequel débouche un canal de fluide (167) relié à la sortie (166) du moyen d'arrêt de reflux (160) à un emplacement d'embouchure (168), de telle sorte que se séparent de l'emplacement d'embouchure (168) une première partie de canal (169) du canal de fluide (167) et une seconde partie de canal (170) du canal de fluide (167), et où est prévu un organe d'arrêt (171) pour fermer la première partie de canal (169) ou la seconde partie de canal (170), et où à l'état fermé de la seconde partie de canal (170), la première entrée (164) du moyen d'arrêt de reflux (160), la première partie de canal (169) et la sortie (166) du moyen d'arrêt de reflux (160) sont reliées fluidement en permettant un écoulement du milieu de pression à la fois de la première entrée (164) du moyen d'arrêt de reflux (160) à la sortie (166) du moyen d'arrêt de reflux (160) et aussi de la sortie (166) du moyen d'arrêt de reflux (160) à la première entrée (164) du moyen d'arrêt de reflux (160), et où inversement, à l'état fermé de la première partie de canal (169), la seconde entrée (165) du moyen d'arrêt de reflux (160), la seconde partie de canal (170) et la sortie (166) du moyen d'arrêt de reflux (160) sont reliées fluidement en permettant un écoulement du milieu de pression à la fois de la seconde entrée (165) du moyen d'arrêt de reflux (160) à la sortie (166) du moyen d'arrêt de reflux (160) et aussi de la sortie (166) du moyen d'arrêt de reflux (160) à la seconde entrée (165) du moyen d'arrêt de reflux (160).
  8. Vérin de verrouillage selon la revendication 6, caractérisé en ce que le moyen d'arrêt de reflux (161) présente une première entrée (164) du milieu de pression, une seconde entrée (165) pour le milieu de pression et une sortie (166) pour le milieu de pression, où la première entrée (164) du moyen d'arrêt de reflux (161) est reliée fluidement avec la sortie (154.1) du premier moyen de maintien de charge - descente freinée (150.1), et où la seconde entrée (165) du moyen d'arrêt de reflux (161) est reliée fluidement avec la sortie (154.2) du second moyen de maintien de charge - descente freinée (150.2), et où la première entrée (164) du moyen d'arrêt de reflux (161) et la seconde entrée (165) du moyen d'arrêt de reflux (161) sont reliées entre elles par un canal de fluide (167) dans lequel débouche un canal de fluide (167) relié à la sortie (166) du moyen d'arrêt de reflux (161) à un emplacement d'embouchure (168) de sorte que se séparent de l'emplacement d'embouchure (168) une première partie de canal (169) du canal de fluide (167) et une seconde partie de canal (170) du canal de fluide (167), et où un premier organe d'arrêt (172.1) est prévu pour fermer la première partie de canal (169) et un second organe d'arrêt (172.2) pour fermer la seconde partie de canal (170), qui ferment la première partie de canal (169) et la seconde partie de canal (170) en ce qui concerne un écoulement du milieu de pression de la sortie (166) du moyen d'arrêt de reflux (161) à la première entrée (164) du moyen d'arrêt de reflux (161) et à la seconde entrée (165) du moyen d'arrêt de reflux (161), et qui permettent un écoulement du milieu de pression de la première entrée (164) du moyen d'arrêt de reflux (161) à la sortie (166) du moyen d'arrêt de reflux (161) et de la seconde entrée (165) du moyen d'arrêt de reflux (161) à la sortie (166) du moyen d'arrêt de reflux (161).
  9. Vérin de verrouillage selon la revendication 4, caractérisé en ce que le milieu de travail ou le milieu de pression est amené au corps de verrouillage (142) respectivement aux corps de verrouillage (142) pour amener celui-ci respectivement ceux-ci dans sa respectivement leur position de déverrouillage, et en ce qu'en même temps le milieu de pression est amené sélectivement à la première chambre de travail (33) ou à la seconde chambre de travail (45) pour provoquer un déplacement du piston (22) dans la première direction (28) ou dans la seconde direction (27).
  10. Vérin de verrouillage selon la revendication 4, caractérisé en ce que le milieu de travail ou le milieu de pression est amené d'abord au corps de verrouillage (42) respectivement aux corps de verrouillage (42) pour amener celui-ci respectivement ceux-ci dans sa respectivement leur position de déverrouillage, et en ce qu'ensuite, le milieu de pression est amené sélectivement à la première chambre de travail (33) ou à la seconde chambre de travail (45) pour provoquer un déplacement du piston (22) dans la première direction (28) ou dans la seconde direction (27).
  11. Vérin de verrouillage selon la revendication 10, caractérisé en ce que le moyen d'arrêt de reflux (156.1, 156.2) présente un organe d'arrêt (173.1, 173.2) pour empêcher un écoulement du milieu de pression de l'entrée (153.1, 153.2) à la sortie (154.1, 154.2) du moyen de maintien de charge - descente freinée respectif (150.1, 150.2) qui peut être chargé par une force d'un ressort (174.1, 174.2) de sorte qu'une ouverture du moyen d'arrêt de reflux (156.1, 156.2) et par conséquent un écoulement du milieu de pression de la sortie (154.1, 154.2) à l'entrée (153.1, 153.2) du moyen de maintien de charge - descente freinée respectif (150.1, 150.2) est possible seulement à partir d'un dépassement d'une pression limite du milieu de pression dont la valeur dépend d'une courbe caractéristique du ressort respectif (174.1, 174.2).
EP04025023A 2003-12-04 2004-10-21 Vérin verrouillable Expired - Lifetime EP1538343B1 (fr)

Priority Applications (1)

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

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DE10356596 2003-12-04
DE10356596A DE10356596B3 (de) 2003-12-04 2003-12-04 Verriegelungszylinder

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

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

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* 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
DE102006030617B4 (de) * 2005-12-29 2009-09-10 Bümach Engineering International B.V. Druckmittelbetriebener Arbeitszylinder mit mechanischer Wegsperrung im drucklosen Zustand
DE202005020365U1 (de) 2005-12-29 2006-02-23 Bümach Engineering International B.V. Druckmittelbetriebener Arbeitszylinder mit mechanischer Wegsperrung im drucklosen Zustand
DE102007024736B3 (de) 2007-05-25 2008-06-12 Neumeister Hydraulik Gmbh Verriegelungszylinder mit Fluidgleitlagerung
DE102016119251A1 (de) * 2016-10-10 2018-04-12 Fbr Facondrehteile Gmbh Hydromechanischer Verriegelungszylinder und hydraulisches Steuersystem zu dessen Betätigung

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* 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
EP0322503A3 (fr) * 1987-12-29 1991-09-25 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
AT4094U1 (de) * 1999-12-07 2001-01-25 Weber Hydraulik Gmbh Linearverstellantrieb

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ES2282778T3 (es) 2007-10-16
DE502004002847D1 (de) 2007-03-22
EP1538343A2 (fr) 2005-06-08
EP1538343A3 (fr) 2005-08-10
ATE353404T1 (de) 2007-02-15
PL1538343T3 (pl) 2007-07-31
DE10356596B3 (de) 2005-06-02

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