Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B66—HOISTING; LIFTING; HAULING
  • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
  • B66F3/00—Devices, e.g. jacks, adapted for uninterrupted lifting of loads
  • B66F3/24—Devices, e.g. jacks, adapted for uninterrupted lifting of loads fluid-pressure operated
  • B66F3/25—Constructional features
  • B66F3/26—Adaptations or arrangements of pistons
  • B66F3/28—Adaptations or arrangements of pistons telescopic
• • 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
  • F15B15/16—Characterised by the construction of the motor unit of the straight-cylinder type of the telescopic type

Definitions

• the invention relates to hydraulic mechanisms of a telescopic type, namely to volumetric power hydraulic motors with rectilinear reciprocating movement of double-acting and can be used in shipbuilding, engineering and other industries.
• Known double-acting telescopic hydraulic cylinders with single-sided rods for implementing large strokes in conditions of insufficient space, which is small for accommodating a conventional translational hydraulic motor (DG), the stroke of which is limited by the length of the assembled cylinder, and in these conditions is always less than the length of the required stroke.
• DG translational hydraulic motor
• Such multi-cylinder hydraulic cylinders comprise a large cylinder in which a large diameter piston is located with a rod having an internal cavity in which a smaller diameter piston with its rod is placed.
• the large cylinder, pistons and rods are concentric and have the possibility of relative and sequential movement, and the sum of their moves is equal to the total stroke of the output link.
• the supply (withdrawal) of the working fluid is simultaneously carried out both to the movable and to the stationary elements, namely, into the common piston cavity and individual rod cavities.
• the disadvantages of the known telescopic hydraulic cylinders are the need to use flexible pipelines that ensure the passage of the working medium to the moving parts of the hydraulic cylinders, as well as the lack of functionality, which is due to the lack of support, in addition to the sequential, also independent action of the stages of the HZ.
• Known telescopic HZ double-acting with one-sided rods, providing simultaneous extension of all stages (Podgorny, Yu.P.
• Hydraulic drives of ground handling aircraft M., Transport, 1980, p.63.65, pic.4.8).
• the hydraulic cylinder consists of a casing and three cylinders, which form three direct pressure chambers and three backpressure chambers, while the counterpressure chamber of the cylinder of the previous stage and the direct pressure chamber of the cylinder of the next stage are pairwise communicated with the formation of a closed joint cavity, which have two cylinders.
• the liquid from the pump in the forward stroke is fed into the direct pressure chamber of the housing.
• check valves mounted in the piston heads except for the piston rod
• From the chamber of the backpressure of the rod liquid is discharged through the rod.
• the fluid is supplied through the rod to the stem counter-pressure chamber, and from the direct pressure chamber formed by the housing, the working fluid is drained into the oil tank.
• TGCD Known double-acting telescopic hydraulic cylinders
• Such TGCD contains a stage in the form of a two-sided rod combined with one of the bodies with ends of different external diameters and a piston in contact with the external body, the working areas of the sides of which are not the same.
• cavities of the hydraulic cylinder stages are pairwise hydraulically connected to form joint cavities.
• Piston cavities of each stage of TGCD are installed with the possibility of their coming into opposite phases, which correspond to the maximum and minimum values of their volumes, in the extreme positions of the hydraulic cylinder.
• TGCD in one of the options are implemented with a minimum total length of telescopic links in the fully extended position of the hydraulic cylinder due to insufficient space.
• the piston is made in the form of a plunger at the internal stage of the double-acting action of TCDC (patent of the Russian Federation Jfs2153464, priority from 08/30/1999, item 27.07.2000).
• a disadvantage of the known TGCD with a minimum total length of telescopic links in the fully extended position of the hydraulic cylinder is that in the initial (retracted) position, at least one of its landing (high-precision) surfaces is open and not protected from external influences. From the above it follows that if in the initial (retracted) position of the telescopic hydraulic cylinder at least one of the landing (high-precision) surfaces is open and not protected from external influences, then in conditions of prolonged exposure to sea water (aggressive environment) and the absence of the possibility of maintenance as well as in the absence of cranking for a long time, corrosion products, salinization, fouling, etc. are collected on the open outer surface (V. Pludek. Corrosion protection at the design stage. M.
• TGCD containing a coaxial set of piston stages, with channels for supplying and discharging the working fluid, with external and internal housings, with one of the steps, comprising a double-sided rod aligned with the internal case, the ends of which have different outer diameters, and a piston made in the form of a sleeve, the working areas of the sides of which are different, mounted on a double-sided rod with the possibility of interaction with it and with the external case, having one bottom on which the end of a two-sided rod of smaller diameter is rigidly fixed.
• TGCD is made with unlike cavities of the mentioned steps, connected hydraulically in pairs with the formation of combined cavities, and with piston cavities that are installed with the possibility of their arrival in opposite phases, corresponding to the maximum and minimum values of their volumes in the extreme positions of the hydraulic cylinder, (application for invention JVy 2006144430 ( 048501) from 12.12.06, the decision to grant a patent from 12.20.07).
• a disadvantage of the known TGCD with a minimum total length of telescopic links in the fully extended position of the hydraulic cylinder is the inadequacy of the total stroke of the hydraulic cylinder due to the stroke of the output link equal to the sum of the moves of each of the links - steps.
• the disadvantage is due to current technological limitations on the length of the mirror treatment of the inner cylindrical surfaces of the inner stage, i.e.
• the objective of the invention is to expand the operational capabilities of the hydraulic cylinder, increasing the efficiency of its use by providing a large value of the total stroke of the hydraulic cylinder in the presence of currently existing technological restrictions on the length of the mirror-machined inner cylindrical surfaces of the hydraulic cylinder with a minimum total length of telescopic links in the fully extended position of the hydraulic cylinder due to insufficient space, the length of which is limited to qil a core (body) with only one internal step extended, which under these conditions provides the necessary total stroke value.
• the objective of the invention is also to simplify the manufacturing technology of the HZ, in particular the housing of the inner stage of the hydraulic cylinder.
• the inner stage is equipped with a hollow cylindrical insert installed rigidly coaxial in the part of the housing having a larger diameter, and a sleeve mounted in the housing with the coverage of the piston and with the possibility of longitudinal movement and sealed th contact with the piston and having
• the ratio of the full stroke of the inner stage to the length of its body, within the course of the stroke and the length of the sleeve with the track support is at least 0.72.
• the length of the area of tight contact of the piston of the inner stage with the sleeve is less than the length of the sleeve.
• the ratio of the length of the sleeve to the length of the housing of the inner stage, within the stroke and the length of the sleeve with the track support is at least 0.5.
• the ratio of the length of the cylindrical insert to the length of the sleeve with the track support is at least 0.75.
• the track support is made in the form of an annular protrusion or end cap with one central hole and at least one hole offset from the center.
• the sleeve is made in the form of a set of hollow cylinders, each of which has a track support.
• the hydraulic connection between the rod cavity of the outer stage and the piston cavity of the inner stage is made in the form of at least one radial channel made in the wall of the housing of the inner stage.
• the technical result of the invention is to optimize the design and reduce the complexity of manufacturing a hydraulic cylinder through the use of a hollow cylindrical insert with an annular neck of such a length that eliminates technological restrictions and facilitate the mechanical processing of hard-to-reach sections of internal surfaces in the manufacture of a hydraulic cylinder.
• the technical result of the invention is also to simplify the manufacturing technology of the housing of the inner stage of the hydraulic cylinder due to the execution of the hydraulic communication channel of the opposite cavity cavities in the wall of the housing of the inner stage short and radial instead of long and longitudinal.
• FIG. L General view of a combined telescopic double-acting hydraulic cylinder for large strokes in the retracted (initial) position; figure 2 - diagram of the hydraulic cylinder in the original, retracted position (the sleeve is made in the form of one hollow hydraulic cylinder);
• FIG.3 the same in an intermediate fixed position; figure 4 is the same in a fully extended position; figure 5 is a diagram of a specific implementation of the hydraulic cylinder with increased stroke in the original retracted position (the sleeve is made in the form of a set of hollow cylinders).
• the combined telescopic double-acting hydraulic cylinder for large strokes (Fig.1,2,3,4) contains a coaxial set of piston stages, which includes a cylindrical housing 1 of the inner
• the set of piston steps also includes a cylindrical housing 3 of the external (large) stage, the piston 4 of the internal (small) stage, rigidly connected to the rod 5 containing channels 6 , 7 for supplying and discharging the working fluid, an elongated piston 8 of an external, large stage, made in the form of a sleeve, having various working areas, mounted on a double-sided rod of the external (large) stage, which is structurally combined with a cylindrical case 1 of the internal (small) stage.
• the piston sleeve 8 is mounted on a double-sided rod - housing 1 with the possibility of interaction with it and with the housing 3 of the external stage.
• the housing 1 of the inner, small stage has cylindrical ends (parts), respectively, 9 of a larger outer diameter and 10 of a smaller outer diameter.
• the rod 5 is installed in the cover 1 1, rigidly fastened to the housing 1, with the possibility of longitudinal movement by the total stroke of the inner stage relative to the cover 1 1.
• the cylindrical insert 2 is made with an annular neck 12.
• a sleeve 13 with a piston 4 The sleeve 13 is installed with the possibility of longitudinal movement and tight contact with the inner surface (inside) - with the piston 4, and the outer surface (outside) - with a cylindrical insert 2 by means of an annular neck 12.
• the length of the region tight contact of the piston 4 of the inner stage with the sleeve 13 is less than the length of the sleeve.
• the sleeve 13 is equipped with a limiter 14 of the piston stroke 14 rigidly connected to it and installed on its inner surface in front of the piston 4 of the piston 4.
• On the cylindrical insert 2 in the form of an annular neck 12 a limiter of the stroke of the sleeve 13 is made.
• the end of the sleeve 13 is made of an annular stop 16, rigidly connected to the track support 15.
• the track support 15 is mounted with relative movement with the rod 5 and is made in the form of an end cap (or an annular protrusion on the surface of the sleeve 13) with one a central opening for the rod 5, and at least one off-center orifice 17.
• track support 15 is up to 3% from the value of this move.
• the ratio of the magnitude of the stroke of the inner stage to the length of its housing 1, within the stroke and the length of the sleeve 13 with the track support 15, is not less than 0.72.
• the ratio of the length of the sleeve 13 to the length of the housing 1 of the inner stage, within the stroke and the length of the sleeve 13 with the track support 15, is at least 0.5, and the ratio of the lengths of the cylindrical insert 2 and the sleeve 13 with the track support 15 is not less than 0.75.
• the piston 8 is slidable on the outer surface of the double-sided rod, combined with the housing 1 of the inner stage and on the inner surface of the housing 3 of the outer stage.
• the telescopic set of steps is made so that it forms a small rod 18 and a large piston 19 cavity of the internal (small) stage, a small 20 and a large 21 cavity of the external (large) stage, while the cavity 18 is in communication with the cavity 21 through channels 22.23.24, and the cavity 19 communicates with the cavity 20 through the radial channel 25 with the formation of the joint cavities.
• the radial channel 25, in the wall of the housing 1 of the inner, small stage is hydraulically connected with the annular gap 26 between the sleeve 13 and the housing 1 of the inner, small stage, while the gap 26 is part of a large piston cavity 19 of the inner, small stage.
• the small cavity 20 of the external, large stage for the functional purpose corresponds to the rod cavity of this stage
• the large cavity 21 of the external, large stage for the functional purpose corresponds to the piston cavity of the same stage.
• Piston cavities of the hydraulic cylinder include piston cavities of each stage, respectively, a large piston cavity 19 of the internal, small stage and a large cavity 21 of the external, large stage.
• the casing 3 of the external (large) stage is made in the form of a glass with one end bottom 27, on which the end 10 (small diameter) of the two-sided rod of the external, large, stage combined with the casing 1 of the internal stage (hereinafter) is rigidly fixed using fasteners 28 - rod-housing 1) while its other end 9, of a larger diameter, is located outside the housing 3.
• the piston 8 of the external (large) stage is made with the ends 9 and 10 of the double-sided rod-housing 1.
• the piston 8 of the external stage is made with unequal working (effective) areas so that p working area the piston from the side of the large cavity 21 exceeds the working area of the piston from the side of the small cavity 20, while, as noted above, the outer diameter of the lower end 9 of the two-sided stem-housing 1 exceeds the outer diameter of its upper end 10.
• the piston 8 forms with a two-sided stem-body 1 of the external, large stage, cavity 20 bounded by cylindrical necks 29 and 30, which are conjugated and interact, respectively, with the cylindrical surfaces of the ends 10 and 9 of the two-sided rod body 1.
• the necks 29 and 30 have different diameters, respectively Corollary diameters double rod-end of the housing 1.
• On the piston 8 is also flange 31, coupled with the inner surface 32 of the outer body 3 steps.
• the piston 8 is made elongated, with a length not less than the stroke of the external, large stage of the hydraulic cylinder, making it possible to tightly contact the outer cylindrical surfaces of the ends 9 and 10 of the two-sided stem-housing 1, and with the inner surface 32 of the housing 3 of the external (large) stage.
• the length of the area of tight contact on the outer surface of the elongated piston 8 is less than the stroke of this (external) stage of the hydraulic cylinder. Otherwise, this area will be exposed to the external environment, which may adversely affect the operational reliability of the hydraulic cylinder.
• the piston 8 of the outer stage is made in the form of a floating stepped sleeve conjugated by means of cylindrical necks 29 and 30 with rod ends of different diameters 10.9, and by means of a shoulder 31 with a cylindrical surface 32 of the outer casing 3.
• the hydraulic cylinder to create a tight contact, is equipped with seals 33, 34, 35, 36, 37, 38, 39, 40, 41.
• a flange 42 is made on the piston 8, which provides the connection of elements of other mechanisms.
• the length of the (external) large stage of the hydraulic cylinder is at least twice the stroke of this stage.
• its length is minimal and limited by a housing with put forward by only one internal (small) step, which under these conditions provides the necessary total amount of stroke, due to the course of the output link, equal to the sum of the moves of each of the links - steps.
• the combined telescopic double-acting hydraulic cylinder is installed in such a way that in the initial position (Fig. 1, 2) the volume of the large cavity 19 of the internal, small stage is minimal, and the volume of the large cavity 21 of the external, large stage is maximum, therefore, the extreme positions of both stages are opposite in phase while the opposite cavity of the hydraulic cylinder is pairwise hydraulically connected with the formation of the joint cavities.
• a sleeve 13 provided with a track support 15 rigidly connected to its annular stop 16 is made in the form of a set of sections — hollow cylinders 43, 44, the latter being equipped with a corresponding track support 45, 47, which are rigidly connected to their respective annular stops 46, 48 on the hollow cylinders 43, 44 and are made, any, with one central hole for the rod 5, and at least one hole offset from the center, respectively, 49. 50.
• the number of sections (hollow cylinders) at the inner (small) stage of the hydraulic cylinder can be different.
• the working fluid under pressure is supplied through channel 6 to the cavity 19 and through an annular gap 26 through channel 25 to the cavity 20, and cavity 21 through channels 24, 23, 22 together with cavity 18 are connected to the drain by channel 7 (Fig. 1).
• the housing 1 and the piston 8 from the initial (retracted) position are successively forced upward.
• the housing 1 is moved until the stop of the cover 1 1 to the end of the sleeve 13 with the track support 15, and then together with the sleeve 13 and the track support 15 to the end of the end face of the piston 4 in the track support 15, and the piston 8 moves inside the housing 3.
• the hydraulic cylinder is installed in extreme extended position, in which the volume of the large cavity 19 is maximum - the combined cavity 19, 20 is connected to the pressure, and the other combined cavity 18, 21 is connected to the drain and the volume of the large cavity 21 is minimal, i.e. the extreme positions of both steps are opposite in phase (Fig. 4).
• the working fluid under pressure is fed through channels 6 and 7 in the cavity 19 and 18, as well as in the cavity 20 and 21 due to the corresponding hydraulic connections of the channels 25 and 22, 23, 24 (figure 2, 4).
• the hydraulic cylinder Under fluid pressure, the hydraulic cylinder is installed in an intermediate fixed position, in which only the housing 1 is extended, the volumes of large cavities 19 and 21 are maximum, the combined cavities are connected with the pressure, i.e. the extreme positions of both stages are single-phase (Fig.Z).
• the movement of the movable elements occurs due to the fact that the working area of the piston 4 from the side of the cavity 19 exceeds the working area from the side of the cavity 18, and the working area of the piston 8 from the side of the cavity 21 exceeds the working area from the side of the cavity 20, i.e. carried out due to the differential principle of the interaction of the moving links. In this way:
• the working fluid under pressure is fed through the channel 7 into the cavity 18 and through the channels 22, 23, 24 into the cavity 21, and the cavity 20 through the channel 25 together with the cavity 19 is connected to the drain channel 6 (Fig. Z, 4).
• the hydraulic cylinder Under the pressure of the liquid, the hydraulic cylinder is installed in the initial (retracted) position, in which the housing 1 and the piston 8 are removed relative to the stationary element — the foundation, the volume of the large cavity 21 is maximum — the combined cavity 18, 21 is connected to the pressure, and the other combined cavity 19, 20 is connected to discharge and the volume of the large cavity 19 is minimal, i.e. the extreme positions of both steps are opposite in phase (Fig. 1, 2).
• the proposed technical solution allows us to expand the operational capabilities of the telescopic hydraulic cylinder, increase its efficiency by expanding the range of preset strokes, as well as to obtain large values of the realized total stroke of the hydraulic cylinder in the presence of technological limitations on the length of the mirror-machined internal cylindrical surfaces, i.e.
• the inventive hydraulic cylinder allows to optimize the design and reduce the complexity of manufacturing a hydraulic cylinder through the use of a hollow cylindrical insert with an annular neck of such a length that eliminates technological limitations and facilitates mechanical processing of hard-to-reach areas of internal surfaces in the manufacture of hydraulic cylinders.
• the presence of a sleeve in the hydraulic cylinder ensures that the hydraulic communication channel of the opposite cavity cavities is short and radial instead of the long and longitudinal in the wall of the inner stage body, which greatly simplifies the manufacturing technology of the body of the internal stage of the hydraulic cylinder in comparison with the closest analogue.
• the maximum outer diameter of the inventive hydraulic cylinder is equal to the maximum outer diameter of the hydraulic cylinder of the closest analogue with the same diameters of the corresponding pistons of these stages.

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• 2008
  • 2008-06-09 CN CN200880129550.6A patent/CN102046985B/zh not_active Expired - Fee Related
  • 2008-06-09 EA EA201001475A patent/EA017689B1/ru not_active IP Right Cessation
  • 2008-06-09 WO PCT/RU2008/000364 patent/WO2009154497A1/ru active Application Filing

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