US3905279A - Piston and cylinder assembly with external mechanical lock - Google Patents

Piston and cylinder assembly with external mechanical lock Download PDF

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Publication number
US3905279A
US3905279A US396857A US39685773A US3905279A US 3905279 A US3905279 A US 3905279A US 396857 A US396857 A US 396857A US 39685773 A US39685773 A US 39685773A US 3905279 A US3905279 A US 3905279A
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United States
Prior art keywords
cylinder
ram
piston
nut
threaded
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US396857A
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English (en)
Inventor
Donald E Yadon
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Eaton Corp
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UNITED HYDRAULICS CORP
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Priority to US396857A priority Critical patent/US3905279A/en
Priority to DE2443284A priority patent/DE2443284A1/de
Priority to FR7431131A priority patent/FR2257803B1/fr
Priority to CA209,354A priority patent/CA1020052A/fr
Application granted granted Critical
Publication of US3905279A publication Critical patent/US3905279A/en
Assigned to CESSNA AIRCRAFT COMPANY, THE, A CORP. OF KS reassignment CESSNA AIRCRAFT COMPANY, THE, A CORP. OF KS ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: UNITED HYDRAULICS CORPORATION
Assigned to EATON CORPORATION, EATON CENTER, CLEVELAND, OH 44114-2584, AN OH CORP. reassignment EATON CORPORATION, EATON CENTER, CLEVELAND, OH 44114-2584, AN OH CORP. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CESSNA AIRCRAFT COMPANY, THE
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    • 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
    • F15B15/202—Externally-operated valves mounted in or on the actuator
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • 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

Definitions

  • a piston and cylinder assembly comprising a cylinder, a piston reciprocable in the cylinder, an elongate ram connected at one end thereof to the piston for movement with the piston and extending at its other end axially outwardly of the cylinder, an abutment fixed in one end of the cylinder against which the piston is engageable to limit outward movement of the piston and ram, an adjustable safety stop carried by the ram externally of the cylinder and manually movable along the length of the ram into engagement with an adjacent end of the cylinder to prevent retraction of said ram into said cylinder, and cooperating structure on said safety stop and said ram to limit inward movement of said safety stop along said ram toward said cylinder so that with said ram-extended and said safety
  • This invention relates to a piston and cylinder assembly having an extensible and retractable ram carried by the piston and a safety mechanical lock means adjustably movable along the ram into engagement with the end of the cylinder for locking the ram against retraction into the cylinder, with the ram in either a fully or partially extended position, to support a load on the ram.
  • the present invention relates to a hydraulically actuated piston and cylinder assembly such as used, for example, in outrigger jacks, or on mobile crane equipment, or back hoes or other machinery, or in retractable dolly wheel assemblies for semitrailers and combination rail and highway travel vehicles and the like, or for crane boom hoist cylinders where exceptionally heavy or dangerous lifts may have to be made, or in any other application where heavy machinery or equipment must be jacked up for servicing or installation positioning, and the like.
  • a hydraulically actuated piston and cylinder assembly such as used, for example, in outrigger jacks, or on mobile crane equipment, or back hoes or other machinery, or in retractable dolly wheel assemblies for semitrailers and combination rail and highway travel vehicles and the like, or for crane boom hoist cylinders where exceptionally heavy or dangerous lifts may have to be made, or in any other application where heavy machinery or equipment must be jacked up for servicing or installation positioning, and the like.
  • a unique and simple hydraulic piston and cylinder assembly which has a double lock valve on one end of the cylinder and with internal ports and oil lines extending from the pilot valve directly into the extend and retract chambers in the cylinder, thus reducing the possibility of damage to the oil lines, as may occur with prior art devices, wherein the oil lines are externally situated.
  • positioning of the double lock pilot valve on the end of the cylinder in the present invention enables a much more compact design to be utilized, with the result that the piston and cylinder assembly can be easily used in many applications where prior art devices are not capable of being used.
  • the mechanical lock nut of the present invention is constructed so that it seats against the end of the cylinder, and it may be constructed to seat against the mounting flange for the cylinder, so that even in the event of failure of the pressure vessel or cylinder itself, or even of the flange mounting welds, the cylinder is not enabled to collapse.
  • the mechanical lock nut is exposed and fully visible to anyone close to the cylinder so that it can be quickly and easily ascertained whether or not the lock nut is in proper positon and, thus, the danger of forgetting to properly position the lock nut, or of obtaining a false impression as to proper position of the lock nut, is eliminated.
  • the cylinder assembly of the present invention is interchangeable with existing devices on jacks and the like and can either be provided as a part of the original equipment or can be an optional sales item or an after market device to place on machines already in the field.
  • the particular construction of the hydraulic cylinder of the present invention enables the lock nut to be removed from the cylinder ram for cleaning or servicing without the necessity of disassembly of the entire hydraulic cylinder, and the ram screw threads can be cleaned and serviced by merely hydraulically extending the ram. Furthermore, the mechanical and hydraulic components of the present invention are completely separated so that contamination due to the wear of the mechanical parts is not transmitted into the hydraulic system and, likewise, any contamination within the hy draulic system is not transmitted intothe mechanical locking arrangement to cause binding or sticking of these components.
  • the construction of the present invention enables the hydraulic cylinder to be used with any type mounting, and particularly with a blind end type mount for application where heavy machinery or buildings must be releveled and mechanically located in their new position.
  • the hydraulic cylinder of the present invention is uniquely constructed such that the ram can be extended outwardly a greater distance than the lock nut can be moved inwardly along the ram, so that the ram can be extended slightly, even with the lock nut moved fully inwardly along the ram, to disengage the lock nut from the end of the cylinder and thus enable the lock nut to'be threaded outwardly along the ram whereby the ram can be retracted into the cylinder.
  • This enables all work tobehydraulically performed, and the lock nut can be easily manually manipulated without requiring excessive force to free the lock nut from the end of the cylinder when a heavy load is resting on the ram.
  • Another object of the invention is to provide a hydraulic piston and cylinder assembly having external mechanical lock means thereon for locking an extensible and retractable ram against retraction in various extended positions thereof, and wherein a double lock pilot valve is used to supply hydraulic pressure fluid to the cylinder to extend and retract the ram and wherein the position of the double lock pilot valve on the cylinder is such as to enable various mounting arrangements for the cylinder, and particularly, a blind end type mounting arrangement.
  • a further object of the invention is to provide a hydraulic piston and cylinder assembly having an extensible and retractable, externally threaded ram with an internally threaded lock nut threaded on the ram externally of the cylinder for engagement with one end of the cylinder to prevent collapse of the cylinder in the event of hydraulic failure and the like, and wherein the ram can be extended outwardly of the cylinder a greater distance than the nut can be threaded inwardly of the ram so that the ram can be extended to disengage the nut from the end of the cylinder and enable the nut to be theaded outwardly along the ram to thus enable the ram to be retracted into the cylinder.
  • a still further object of the invention is to provide a hydraulic piston and cylinder assembly having an external safety lock nut thereon, wherein the lock nut can be easily removed for cleaning or servicing without requiring disassembly of the entire piston and cylinder assembly, and the piston and cylinder assembly can be easily assembled and disassembled for service or cleaning.
  • FIG. 1 is a perspective view of the hydraulic piston and cylinder assembly of the present invention showing the ram in its fully extended position.
  • FIG. 2 is a greatly enlarged end view of the assembly of FIG. 1, showing the double lock pilot valve on one end of the cylinder.
  • FIG. 3 is an enlarged, exploded, persepective view of the piston and cylinder assembly of the present invention showing the various components thereof.
  • FIG. 44' is an enlarged sectional view in elevation with portions broken away of the piston and cylinder assembly in a fully retracted, rest position with both valves of the double pilot lock valve in closed position,
  • FIG. 5-5 is a view similar to FIG. 4-4 with hydraulic fluid being admitted to the cylinder through the double lock pilot valve and with the ram partially extended and the lock nut carried outwardly therewith.
  • FIG. 6 is a view in elevation with portions broken away and portions shown in section of the piston and cylinder assembly in fully extended position and with the lock nut threaded along the ram into engagement with one end of the cylinder to prevent collapse of the cylinder in the event of hydraulic line failure and with the double lock pilot valve shown in closed position to effect a hydraulic lock,
  • FIG. 7 is a greatly enlarged, fragmentary sectional view with portions broken away of the piston and cylinder assembly of the invention showing the lock nut threaded fully inwardly along the ram, but with the ram extended outwardly its full limit of travel to disengage the lock nut from the end of the cylinder so that the lock nut can be easily manually threaded outwardly along the ram to enable retraction of the ram into the cylinder.
  • FIG. 8 is a view similar to FIG. 7 with pressure fluid being admitted through another of the valves of the double pilot lock valve into the cylinder to retract the ram into the cylinder.
  • the hydraulic piston and cylinder assembly of the invention is indicated generally at 10 and comprises an elongate cylinder 11 having opposite open ends 12 and 13 and an inner surface 14.
  • the inner surface 14 of the cylinder 11 at open end 13 is slightly diametrically enlarged and threaded as at 15 and the threaded portion 15 is joined to the inner surface 14 by an inwardly sloping, conically shaped portion 16 to facilitate assembly of the components of the invention and to prevent damage to seal means for the piston by the threads 15 when the components are assembled.
  • a circular, disc-shaped end closure or cylinder cap 17 is suitably secured in the open end 12 of cylinder 11, as by means of a weld W or the like, and the weld preferably comprises a J-type weld to relieve stress risers and the like.
  • the closure 17 has parallel, planarinner and outer faces 18 and 19, respectively, and a central opening 20 therethrough extending between faces 18 therethrough and the port 22 is closed at .its outer end by a threaded. plug 23.
  • An axiallyextending fluidport 24 extendsfrom face 19 to the port 22 intermediate the central opening and outer surface of closure 17. and a second fluid port.25 extends between faces 18 and 19 intermediate the outer surface of the closure. 17 and the 1 central opening 20 therethrough on the diametrically opposite side of closure from port 24..-
  • I 1 An elongate, cylindrical tube- 26 having opposite open ends 27 and 28 and an inner surface29 is fitted at one end thereof in the bore 20 through closure 17* and extends at its other-end outwardly beyond'the open end 13 of cylinder 11. Said one --end 27.0f the tube 26 is closed by a solid cylindrical'plug 20 secured in the open end, as by means of a weld W- or .the like, with said plug flush with said one end of said tube.
  • a radially extending port 31 extends through the sid of tube 26 in registry with port 22 in endclosure 17 and a snap ring 32 is received over said one end of the tube 26 in the recess 21 to hold the tube in the position shown in FIG. 44"with the ports 31 and 22 in registry.
  • a pair of seal receiving channelsori grooves 33 are formed in the bore 20 of closure 17 and a pair of sealing rings 34 are positioned inthe channelson opposite sides of the port'22 foreffectinga fluid tight seal between the -tube 26 and closure 17..
  • a similar solid, cylindrical plug 35 is suitably secured within the open end 28 of tube 26, as by means of a weld W or the like, for closing the other open end of the tube 26.
  • An annular, combination seal and spacer ringor bushing 36 is suitably secured to the outer surface of said other end of the tube 26, between a retaining ring 36' welded to the end of tube 26 as at W, and a snap mounting rings oryvashers 48 and, 49 clamped between ,the sl'ioulder 46 and a snap ring SO spaced axially from the shoulde r 46.
  • Th e ririg 47 is slidably sealed to the .t ube 26 by, means of an annular sealring 51 carried in a seal ring receiving groove 52 in the inner surface of ring 47, and,the ring 47 is sealed to the ram 41 by means of a ring 53 vcarried in a groove 54in the outer surface of ring 47, 'l"he tube 26, ram41, seal ring 36 or piston means 47 define a retract chamber 55 therebetween, to which pressure fluid is admitted to act against the ring or piston means47 and draw or retract the ram 41 into the cylinder.
  • a radial port 56 extends through the tube 26 adjacent the open end 28 thereof but spaced axially inwardly from the ring 36 for admitting and exhausting pressure fluid to and from the re- .tract chamber 55.
  • I v v Theouter surface of the inner end. of ram 41 is recessed at 57 defining an axially facing shoulder 58, and
  • a combination seal and spacing ring or piston means 59 is; carried by the ram in said recessand is held in position in the recess betweenan annular clamping ringor washer 60 abutted against shoulder 58, and a snap ring engagement withthe surface of cylinder 11 and a plurality of seal ring receiving channels 64 are in the outer ring 32- on the tube 26 spacedaxially inwardly from ring 36.
  • Th'e combination seal and spacer ring 36 has A plurality of axially spaced seal ring receiving chan nels or grooves 29 are also formed in the outer surface of the ring 36 and wiper and sealing ring means--40 are positioned in the seal receiving grooves 39.
  • An elongate, cylindrical, extensible and retractable ram 41 is telescopically received within the cylinder 1 1 in radially outwardly spaced relationship to the tube 26 and radially inwardly spaced relationship tothe inner surface 14 of cylinder 1.
  • the ram 41 has a cylindrical inner surface 42 slidably received on the ring-.36 and the seal rings 40 carried by the ring 36 effect a fluid tight seal between the ram 41 and the ring36.
  • the ram 41 has an open'inner end 43 and an open outer end 44 spaced axially outwardly of the end 13of cylinder '1 l.
  • the open inner end 43 of the ram 41 is diametrically enlarged relative to the inner surface 42 and is joined to-thc surface 42 by a conically flar'edportion 45, the
  • ring or piston means 59 is'sealed to the inner end of ,ram 41 by means of an O-ring 66 or the like carried in a channel 67in the inner surface of ring 59.. v i
  • seal and spacer rings, or piston means, 47' and 59, the inner surface 14 of cylinder 11, the outer surface of tube 26, and theinne'r face 18 of closure 17 define an extend chamber 68 to which pressure fluid is admitted through port 25 in the end closure 17 for exeffect, a piston means for the ram 41.
  • the outer surface of the ram 41 is threaded as at 69 from a point spaced axially from the clamp ring 60 to -the outer end of the ram.
  • An abutment means comprising an annular'guide ring or bushing 70 has an externally threaded portion 71 thereonv threadably engaged I wwith the threads15 in the open end 13 of cylinder 11 andhas a cylindericalinner surface 73 slidably engaged with the outer surface of the ram 41 for guiding the outer end of the ram in its movement relative to the cylinder 11.
  • A. plurality of tool engaging openings 74 are in the outer end surface of the guide sleeve or bushing 70 for attaching and removing the guide sleeve from the open end of cylinder 1 1
  • the inner end of guide sleeve 70 has an axially facing shoulder 75 thereon defining a positive stop or abutment for limiting outward travel of the piston meansand ram and against when the ring 60 abuts at the extreme limit of travel of the ram in its extended position
  • a safety lock nut 76 is threadably engaged on the ram 41 axially outwardly of the cylinder 1 1 and has internal threads 77 therein matingly engaged with the threads 69 on ram 41, so, that the nut 76 may be easily a ,manually threaded along the ram 41 into and out of engagementwith the outer end surface of the cylinder 1.
  • the outer surface of the nut 76 is knurled as at 78 so that a more secure grip thereon can be effected, and an annular stop plate 79 is secured to the outer end surface of the nut 76 by means of a plurality of cap screws 80 or the like extended through the plate 79 and into the nut 76.
  • the nut 76 is retained against accidental axial displacement from the end of ram 41 by means of a snap ring 81 or the like positioned on the outer end of ram 41.
  • a combination felt oiler and wiper ring 82 is positioned in one of the thread grooves in the ram 41 for cooperation with the inner surface of lock nut 76 to be moved along the threads of the ram nut 76 to clean and lubricate the threads.
  • the length of the unthreaded portion of ram 41 between the inner end of threads 69 and the outer end surface of ring is greater than the distance or length of bushing between the abutment surface and the outer end surface thereof, so that with the ram fully extended and the piston means abutting the abutment surface 75, the nut 76 is disengaged from the end of the cylinder, or conversely, when the nut 76 is threaded all the way in along threads 69 and into engagement with the end of cylinder 11, the piston means or ring 60 is spaced from abutment surface 75, and the piston means may thus be moved farther outwardly and into engagement with abutment 75 to disengage nut 76 from the end of cylinder 11 to thus enable the nut to be easily manually threaded outwardly along the ram and consequently the ram can be retracted into the cylinder.
  • An annular mounting flange 86 is suitably secured to the outer surface of cylinder 11 adjacent the open end 13 thereof, as by means of a pair of welds W on opposite sides thereof, and a plurality of axially extending, circumferentially spaced openings 87 extend through the mounting flange 86 for receiving bolts or the like (not shown) therethrough to mount the cylinder and piston assembly to a desired supporting structure.
  • the lock nut 76 may be larger in diameter than the outer diameter of cylinder 11, so that the lock nut would be engageable with the mounting flange 86 to prevent collapse of the cylinder in the event of failure of the welds W by which the mounting flange is secured to the cylinder.
  • An oil fitting 88 is threadably attached to a tapped opening 89 in the side of cylinder 41 adjacent the guide sleeve 70 therein, by means of which the combination oiler and wipe ring 62 may be lubricated when the ram is in its extended position, as seen in FIG. 6, for example.
  • a double lock pilot valve 90 for controlling the-supply and exhaust of pressure fluid to and from the entend and retract chambers 68 and 55, respectively, is suitably secured to the outer surface or face 19 of cylinder cap or end wall 17 and comprises a valve block 91 having a transverse bore or passageway'92 therethrough, with diametrically enlarged, internally threaded opposite ends 93 and 94.
  • a pair of ball valve assemblies and 96 are removably threaded engaged in the opposite threaded ends 93 and 94 of passage 92 in block 91, and the ball valve assemblies 95 and 96 are substantially identically constructed, and each comprises a valve housing or body 97 having an axially extending bore 98 therein and a transversely extending bore 99 opening through the sides of the housing and communicating with the bore 98 substantially intermediate the ends thereof.
  • Each ball valve assembly 95 and 96 includes a valve seat 102, which may be constructed with two symmetrical seating surfaces 102a and 102b on respective opposite sides thereof, see FIG. 5, and thus be reversible, if desired, in order to provide a built in spare seat for replacement of a worn seat, or the like.
  • the seat is at the housing 97 adjacent the inner end thereof in surrounding relationship to the bore 98 therein, and ball valves 103 and 104 are positioned in the assemblies 95 and 96, respectively, for cooperation with the valve seats 102, and the ball valves 103 and 104 are urged toward their closed position against the seat by means of a coil spring 105 engaged between the ball and the closed end of bore 98 in the housing 97.
  • a stop element 106 is in each housing 97 rearwardly of the balls 103 and 104 to provide a positive stop against which the ball engages at its maximum open position.
  • Annular sealing rings 107 are positioned in seal ring receiving grooves in the inner surface of valve block 91 and are positioned in surrounding relationship to the ports 100 and 101, respectively, to effect a fluid seal between the valve block 91 and cylinder cap 17.
  • Housing 97 and seats 102 of ball valve assemblies 95 and 96 are also each suitably sealed in their respective end of the bore 92 by means of sealing rings 108 and 109, respectively, engaged between the housings 97 and seats 102 and adjacent portions of bore 92.
  • a piston 1 10 is slidably positioned in bore 92 and has a pair of elongate, axially extending ball actuating pins 111 and 112 on opposite ends thereof for engaging a respective ball 103 or 104 to unseat that ball when fluid pressure is admitted to the bore 92 on the'opposite end of the piston 110.
  • a transverse, fluid inlet and outlet port 113 is in the valve block 91 inwardly of valve assembly 95 and extends through the block into communication with the bore .92 between the piston and ball valve 103 for admitting and exhausting pressure fluid to the bore 92 and past the valve 103 through the bore 100 and bore 24 and thence to the transverse bore 22 and through port 31 into the hollow interior of tube 26, from which the fluid passes through port 56 into the retract chamber 55 to retract the ram into the cylinder.
  • Pressure fluid entering port 113 also acts against piston 110 and moves it downwardly and the pin 112 engages ball 104 and unseats ball 104 to exhaust fluid from the extend chamber 68.
  • a fluid inletand outlet port 114 is formed in valve block 91 in communication with the bore 92 in the valve block at the opposite end of the piston 110, between the piston and ball valve 104, and through which the fluid is exhausted from the. extend chamber 68 when fluid is introduced through port 1 13 to retract the ram.
  • a thermal relief bypass ball valve assembly 115 is threadably secured in a bore 116 in the valve block 91 adjacent valve assembly 95 and includes a ball valve 117 biased to seat against a valve seat in a passage 118 communicating with opposite sides of the ball 103 so that the ball 117 is normally closed upon the introduction of pressure fluid to port 113, but is enabled to be opened by an increase in pressure of the fluid in retract chamber 55 above a predetermined value when the fluid is heated and thus expands, to prevent damage to the piston and cylinder assembly. Only a small amount of fluid is vented from the retract chamber, and this enables the piston to move and thus slightly expand the expand chamber to relieve pressure in the device. No pressure fluid is vented from the expand side of the piston, and the minute movement of the piston upon venting of a small amount of fluid from the retract chamber is sufficient to protect the assembly.
  • the double pilot lock valve 90 is secured to the surface 19 of end cap 17 on cylinder 11 by means of a plurality of bolts 119 extended through the block 91 into the end cap 17.
  • a fluid inlet fitting 120 is connected with the block 91 in communication with port 113 for admitting and exhausting pressure fluid to and from the double pilot lock valve and thus to and from the retract chamber 55, and a fluid inlet fitting 121 is similarly connected with port 1 14 for supplying and exhausting pressure fluid to and from the extend chamber 68.
  • the device of the present invention is shown at rest in FIG. 4-4 and no pressure fluid is being supplied to the ports 113 and 114 and both balls 103 and 104 are closed. Also, the ram 41 is in its fully retracted position, with the inner end of ram 41 abutting against the inner surface 18 of end cap or closure 17. The nut 76 is threaded completely out on the end of ram 41 against the snap ring 81 and is in engagement with the outer end of cylinder 11.
  • pressure fluid is being supplied to port 114 through inlet fitting 121 and the pressure fluid has unseated ball 104 and is passing though ports 101 and into extend chamber 68 through is acting against the piston means 47 and 59 to extend the ram axially outwardly of the cylinder 11.
  • the ram is only partially extended and the lock nut 76 is being carried outwardly with the ram.
  • the pressure fluid entering bore 92 through port 114 has moved the piston 1 l0 upwardly and the pin 1 11 on the piston is engaged with ball 103, unseating ball 103, so that the fluid within retract chamber 55 is exhausted through the hollow interior of tube 26 and through the ports 22,
  • the ram may be mechanically locked against retraction in the partially extended position of FIG. 5-5' by threading the lock nut 76 inwardly along ram 41 into engagement with the end of cylinder 1 1 as indicated in phantom lines at 76'.
  • the ram is shown in its substantially fully extended position and no pressure fluid is being admitted to the double pilot lock valve and both ball valves 103 and 104 are, therefore, in their seated position.
  • the fluid is trapped in both the extend and retract chambers and a hydraulic lock is effected to maintain the ram in its extended position.
  • the nut 76 is threaded fully inwardly along ram 41 against the end of cylinder 1 1 to provide a mechanical lock so that the ram will not retract into the cylinder under a compressive loading in the event of failure in the hydraulic system for the ram.
  • the ring 60 is spaced a slight distance from the guide sleeve and abutment 75.
  • the combination oiler and wiper ring 62 is disposed immediately adjacent the oil fitting 88 and it is in this position that the oil is admitted through the fitting 88 to lubricate the piston and cylinder assembly of the present invention.
  • pressure fluid is once again being admitted through port 114 and into the extend chamber 68 to move the ram axially outwardly the remaining slight distance between the ring 60 and sleeve 70 to disengage the nut 76 from the end of cylinder 11 so that the nut 76 may be easily manually threaded outwardly along the ram 41 to enable the ram to then be retracted into the cylinder.
  • FIG. 8 the double pilot lock valve is shown in the retract position with pressure fluid being admitted through port 113 and past ball valve 103 through ports 100, 24, 22 and 31 into the interior of tube 26 and thence through port 56 into the retract chamber 55 to act against the ring or piston means 47 to urge the ram 41 axially inwardly of the cylinder 11, as indicated by the arrows.
  • the piston moves downwardly, with pin 112 unseating ball 104, and the fluid in the extend chamber 68 is exhausted through ports 25 and 101 and past ball 104 to and through port 114.
  • the lock nut 76 is threaded outwardly along the ram 41 away from the cylinder 11 in order to enable the ram to be retracted into the cylinder.
  • the lock nut when threaded against the end of the cylinder, will prevent accidental retraction of the ram into the cylinder even if the hydraulic system is actuated to retract the ram.
  • the unique structure of the piston and cylinder assembly of the present invention results in a compact, rugged design, which is durable in operation and which may be utilized in a variety of applications where prior art devices could not be used, and the unique external safety lock nut arrangement of thepresent invention enables the device to be used in any desired position and provides a simple, effective means of preventing accidental collapse of the hydraulic cylinder assembly under compressive loading, and the position of the lock nut is readily visually observable.
  • a piston and cylinder assembly as in claim 2, wherein said cooperating means to limit inward movement of said nut alongsaid ram toward said cylinder comprises an unthreaded portion of the ram at said one end of the ram, at leasta part of said unthreaded portion being disposed outwardly of the end of the cylinder in the fully extended position of the ram,

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
US396857A 1973-09-13 1973-09-13 Piston and cylinder assembly with external mechanical lock Expired - Lifetime US3905279A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US396857A US3905279A (en) 1973-09-13 1973-09-13 Piston and cylinder assembly with external mechanical lock
DE2443284A DE2443284A1 (de) 1973-09-13 1974-09-10 Zylinder/kolben-anordnung mit einer aeusseren mechanischen verriegelung
FR7431131A FR2257803B1 (fr) 1973-09-13 1974-09-13
CA209,354A CA1020052A (fr) 1973-09-13 1974-09-13 Groupe piston/cylindre a verrouillage mecanique externe

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US396857A US3905279A (en) 1973-09-13 1973-09-13 Piston and cylinder assembly with external mechanical lock

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US3905279A true US3905279A (en) 1975-09-16

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US (1) US3905279A (fr)
CA (1) CA1020052A (fr)
DE (1) DE2443284A1 (fr)
FR (1) FR2257803B1 (fr)

Cited By (21)

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US4073345A (en) * 1977-02-14 1978-02-14 Miller Maurice E Disc harrow wheel lock-down with depth control adjustment structure
US4367674A (en) * 1979-02-23 1983-01-11 Aisin Seiki Kabushiki Kaisha Actuator device
EP0099700A1 (fr) * 1982-07-07 1984-02-01 Hydra-Jack, Inc. Vérin de stabilisation à verrouillage mécanique pour assemblage de stabilisation
US4463659A (en) * 1983-10-27 1984-08-07 Deere & Company Cylinder stroke limiter
US4469014A (en) * 1983-06-13 1984-09-04 Deere & Company Cylinder spacer
US4641725A (en) * 1984-08-27 1987-02-10 Conoco Inc. Wide dynamic range hydraulic vibrator
US4787781A (en) * 1987-05-14 1988-11-29 Walter Lipscomb Shoring device
EP0508778A1 (fr) * 1991-04-12 1992-10-14 P.L. Porter Company Limiteur de la course continûment ajustable pour un positionneur hydraulique
US5499890A (en) * 1994-07-08 1996-03-19 Americ Corporation Trench shoring device with locking mechanism
US5513555A (en) * 1994-01-21 1996-05-07 Michael J. Plank Quick-release cam lock with locking pin
US5868060A (en) * 1994-01-24 1999-02-09 Speed Shore Corp. Quick-release cam lock
WO2000025028A1 (fr) * 1998-10-23 2000-05-04 General Signal Corporation Dispositif de blocage pour actionneurs
US6282893B1 (en) 1999-08-19 2001-09-04 Delaware Capital Formation, Inc. Self-contained actuator
US6516706B2 (en) 1999-08-19 2003-02-11 Delaware Capital Formation, Inc. Actuator having internal valve structure
US20100213154A1 (en) * 2009-02-20 2010-08-26 Terex Demag Gmbh Locking and bolting unit
US20110016881A1 (en) * 2009-07-21 2011-01-27 Jose Luis Ruiz Gas turbine with exhaust gas casing and method for producing a gas turbine
US20130247753A1 (en) * 2012-03-22 2013-09-26 Actuant Corporation Fluid Cylinder Assembly Having Automatic Stroke Shutoff
US20140157746A1 (en) * 2012-12-06 2014-06-12 Cnh America Llc Automatically engaging and disengaging header lock assembly
US10018009B2 (en) * 2015-02-26 2018-07-10 Cameron International Corporation Locking apparatus
US10287837B2 (en) * 2016-08-02 2019-05-14 Cameron International Corporation Hydraulic timing device
US10493600B2 (en) * 2014-02-14 2019-12-03 Safran Aircraft Engines System for clamping a part and method for sealing the inner casing of a low pressure rectifier of a turbomachine

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Publication number Priority date Publication date Assignee Title
DE2826610A1 (de) * 1978-06-19 1980-01-03 Bosch Gmbh Robert Ventilanordnung fuer einen hydraulischen verbraucher

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US2408181A (en) * 1942-01-22 1946-09-24 Joyce Cridland Co Lifting mechanism
US2736294A (en) * 1951-08-09 1956-02-28 Smith Corp A O Adjustable stroke ram and piston assembly
US3005669A (en) * 1959-10-23 1961-10-24 Galland Henning Mfg Company Fluid pressure cylinder
US3045649A (en) * 1960-11-29 1962-07-24 Leland F Blatt Double acting tool and die cylinder
US3141390A (en) * 1960-09-20 1964-07-21 Symington Wayne Corp Lifting device
US3301140A (en) * 1965-05-03 1967-01-31 Duff Norton Co Expansible shielding means
US3335642A (en) * 1965-01-08 1967-08-15 Borje O Rosaen Cylinder construction
US3407710A (en) * 1966-12-14 1968-10-29 Alpha Press Company Stroke adjustment means for cylinder and piston assembly
US3420148A (en) * 1965-03-12 1969-01-07 Richard E Doerfer Holding device

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US38606A (en) * 1863-05-19 Improvement in hydraulic presses
US1711549A (en) * 1926-11-08 1929-05-07 Watson Stillman Co Hydraulic jack
US2408181A (en) * 1942-01-22 1946-09-24 Joyce Cridland Co Lifting mechanism
US2736294A (en) * 1951-08-09 1956-02-28 Smith Corp A O Adjustable stroke ram and piston assembly
US3005669A (en) * 1959-10-23 1961-10-24 Galland Henning Mfg Company Fluid pressure cylinder
US3141390A (en) * 1960-09-20 1964-07-21 Symington Wayne Corp Lifting device
US3045649A (en) * 1960-11-29 1962-07-24 Leland F Blatt Double acting tool and die cylinder
US3335642A (en) * 1965-01-08 1967-08-15 Borje O Rosaen Cylinder construction
US3420148A (en) * 1965-03-12 1969-01-07 Richard E Doerfer Holding device
US3301140A (en) * 1965-05-03 1967-01-31 Duff Norton Co Expansible shielding means
US3407710A (en) * 1966-12-14 1968-10-29 Alpha Press Company Stroke adjustment means for cylinder and piston assembly

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4073345A (en) * 1977-02-14 1978-02-14 Miller Maurice E Disc harrow wheel lock-down with depth control adjustment structure
US4367674A (en) * 1979-02-23 1983-01-11 Aisin Seiki Kabushiki Kaisha Actuator device
EP0099700A1 (fr) * 1982-07-07 1984-02-01 Hydra-Jack, Inc. Vérin de stabilisation à verrouillage mécanique pour assemblage de stabilisation
US4469014A (en) * 1983-06-13 1984-09-04 Deere & Company Cylinder spacer
US4463659A (en) * 1983-10-27 1984-08-07 Deere & Company Cylinder stroke limiter
US4641725A (en) * 1984-08-27 1987-02-10 Conoco Inc. Wide dynamic range hydraulic vibrator
US4787781A (en) * 1987-05-14 1988-11-29 Walter Lipscomb Shoring device
GB2204621B (en) * 1987-05-14 1991-09-04 George Bradberry Shoring device
EP0508778A1 (fr) * 1991-04-12 1992-10-14 P.L. Porter Company Limiteur de la course continûment ajustable pour un positionneur hydraulique
US5513555A (en) * 1994-01-21 1996-05-07 Michael J. Plank Quick-release cam lock with locking pin
US5868060A (en) * 1994-01-24 1999-02-09 Speed Shore Corp. Quick-release cam lock
US5499890A (en) * 1994-07-08 1996-03-19 Americ Corporation Trench shoring device with locking mechanism
WO2000025028A1 (fr) * 1998-10-23 2000-05-04 General Signal Corporation Dispositif de blocage pour actionneurs
US6105484A (en) * 1998-10-23 2000-08-22 Kalthoff; Gene Lockout device for valve actuators
US6282893B1 (en) 1999-08-19 2001-09-04 Delaware Capital Formation, Inc. Self-contained actuator
US6516706B2 (en) 1999-08-19 2003-02-11 Delaware Capital Formation, Inc. Actuator having internal valve structure
US6530220B2 (en) 1999-08-19 2003-03-11 Delaware Capital Formation, Inc. Elongated self-contained actuator
US9090438B2 (en) * 2009-02-20 2015-07-28 Terex Cranes Germany Gmbh Locking and bolting unit
US20100213154A1 (en) * 2009-02-20 2010-08-26 Terex Demag Gmbh Locking and bolting unit
US20110016881A1 (en) * 2009-07-21 2011-01-27 Jose Luis Ruiz Gas turbine with exhaust gas casing and method for producing a gas turbine
US20130247753A1 (en) * 2012-03-22 2013-09-26 Actuant Corporation Fluid Cylinder Assembly Having Automatic Stroke Shutoff
US20140157746A1 (en) * 2012-12-06 2014-06-12 Cnh America Llc Automatically engaging and disengaging header lock assembly
US8931246B2 (en) * 2012-12-06 2015-01-13 Cnh Industrial America Llc Automatically engaging and disengaging header lock assembly
US9380744B2 (en) 2012-12-06 2016-07-05 Cnh Industrial America Llc Automatically engaging and disengaging header lock assembly
US10493600B2 (en) * 2014-02-14 2019-12-03 Safran Aircraft Engines System for clamping a part and method for sealing the inner casing of a low pressure rectifier of a turbomachine
US10018009B2 (en) * 2015-02-26 2018-07-10 Cameron International Corporation Locking apparatus
US10287837B2 (en) * 2016-08-02 2019-05-14 Cameron International Corporation Hydraulic timing device

Also Published As

Publication number Publication date
FR2257803A1 (fr) 1975-08-08
CA1020052A (fr) 1977-11-01
FR2257803B1 (fr) 1978-06-09
DE2443284A1 (de) 1975-03-20

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Effective date: 19880930