US3864922A - Sealed cushioning unit - Google Patents

Sealed cushioning unit Download PDF

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Publication number
US3864922A
US3864922A US453980A US45398074A US3864922A US 3864922 A US3864922 A US 3864922A US 453980 A US453980 A US 453980A US 45398074 A US45398074 A US 45398074A US 3864922 A US3864922 A US 3864922A
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Prior art keywords
cylinder
piston
piston body
marine
end wall
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Expired - Lifetime
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US453980A
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English (en)
Inventor
Darrell D Dial
Bose Robert J Von
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Halliburton Co
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Halliburton Co
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Priority to US453980A priority Critical patent/US3864922A/en
Priority to US05/538,803 priority patent/US4043545A/en
Application granted granted Critical
Publication of US3864922A publication Critical patent/US3864922A/en
Priority to JP3287475A priority patent/JPS5526246B2/ja
Priority to DE19752511965 priority patent/DE2511965A1/de
Priority to DE19752548410 priority patent/DE2548410C3/de
Priority to FR7508931A priority patent/FR2274738A1/fr
Priority to IT21529/75A priority patent/IT1034494B/it
Priority to GB12010/75A priority patent/GB1500074A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02B—HYDRAULIC ENGINEERING
    • E02B3/00—Engineering works in connection with control or use of streams, rivers, coasts, or other marine sites; Sealings or joints for engineering works in general
    • E02B3/20—Equipment for shipping on coasts, in harbours or on other fixed marine structures, e.g. bollards
    • E02B3/26—Fenders
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/30—Adapting or protecting infrastructure or their operation in transportation, e.g. on roads, waterways or railways

Definitions

  • ABSTRACT A method and apparatus for cushioning motion and dissipating impact energy, preferably in a marine environment, including a piston and cylinder assembly, impedance means associated with the piston and cylinder for impeding translation of the piston within the cylinder assembly and an isolation and restoring assembly protectively surrounding the piston and cylinder assembly and continuously biasing the piston and cylinder assembly in a normally extended position operable to dissipate impact energy.
  • the method includes the steps of isolating the piston and cylinder assembly from an ambient environment, cushioning impact forces imparted to the piston and cylinder assembly 16 Claims, 16 Drawing Figures [52] US.
  • This invention relates to a method and apparatus for dissipating impact energy between relative converging members. More particularly the invention relates to a method and apparatus for dissipating energy imparted to a protective marine bumper from impact forces imparted thereto by a floating vessel or the like.
  • fendering or protective bumper system In the past in both onshore and offshore locations some form of fendering or protective bumper system has been utilized to dissipate kinetic energies imparted from a floating vessel into a relatively stationary mooring or berthing facility. Such devices may range from the expedient utilization of a worn out tire casing to elaborate elastomeric cellular fendering units of a variant and often intricate configuration.
  • the subject invention is directed to an improved method and apparatus for dissipating energy, preferably in a marine bumper system, wherein a piston and a cylinder assembly is connected at the ends thereof between a protective bumper and a marine installation such as an onshore pier, an offshore berthing dolphin, an offshore tower leg, etc.
  • the hydraulic cylinder is comprised of an inner generally circular high pressure cylinder which is operable to receive in intimate translation a piston body.
  • the high pressure cylinder is provided with a plurality of radially extending exponentially spaced metering ports whereby fluid from within the interior of the cylinder may be metered into a surrounding low pressure return chamber formed by a relatively thin cylindrical wall coaxially mounted about the high pressure cylinder.
  • Such low level impedance is highly effective to dissipate cyclic wave action induced forces.
  • each of the present check valve units has maximum capacity limits and is operable toiaccommodate extremely high level impact forces which may be occasioned during an accidental high velocity berthing operation.
  • the hydraulic cushioning assembly is isolated from a hostile ambient marine environment by the provision of an encapsulating cylindrical housing connected at the ends thereof to the hydraulic unit through annular generally frustoconically shaped elastomeric members.
  • the isolation housing is axially dimensioned so as to place the elastomeric units under bending and shear loading even during full extension of the hydraulic cushioning unit. Accordingly once impact energy forces have been dissipated by metering of fluid through the hydraulic cylinder wall, restoring forces provided by the flex and shear of the elastomeric units rapidly restore the cushioning unit to an extended posture ready to receive and dissipate further impact ener-- gies.
  • a further metering port is positioned adjacent the restoring end of the cylinder to eliminate any rapid rebound energy from the elastomeric members.
  • the method entails the steps of isolating the piston and cylinder assembly from a hostile corrosive marine environment while cushioning low level impact forces against the marine protective bumper by flexing and shearing the elastomeric annulus members and translating the piston body within the high pressure cylinder.
  • the method further includes the steps of restoring the piston body to a position of axial extension byapplication of the developed flex and shear of the elastomeric annulus memberswhile metering fluid from behind the piston body through the wall of the high pressure fluid cylinder. Such metering of fluid during the restoration step effectively minimizes or eliminates the possibility of rebound energy being input to the floating vessel.
  • the exterior housing effectively isolates the hydraulic cushioning unit from a hostile and corrosive marine environment while synergistically providing a highly efficient restoring mechanism for maintaining the cushioning unit in an extended posture operable to receive and dissipate impact energy.
  • THE DRAWINGS and moored vessel positioned adjacent the dolphin and being spaced therefrom by a protective bumper system including a plurality of energy dissipating devices according to a preferred embodiment of the invention
  • FIG. 2 note sheet 2, is a side elevational detailed view, partially broken away, disclosing an energy dissipating and cushioning unit according to a preferred embodiment of the invention in a fully extended posture operable to receive and dissipate impact energy;
  • FIG. 3 is a side elevational detailed view, partially broken away, disclosing the energy dissipating and cushioning unit, disclosed in FIG. 2, in a fully compressed or buff posture as might exist immediately following dissipation of kinetic energy and prior to automatic restoration of the unit to an extended or restored posture, as depicted in FIG. 2;
  • FIG. 4 note sheet 1 is a cross-sectional view taken along section line 4-4 in FIG. 2 and discloses structural details of a high pressure circular cylindrical side wall and a generally square fluid-tight surrounding housing comprising a portion of the hydraulic cushioning unit;
  • FIG. 5, note sheet 3 is a top view of a preset check valve positioned within a plurality of ports extending through the high pressure cylinder wall;
  • FIG. 6 is a sectional detailed view taken along section line 66 of FIG. and discloses the relationship of components within the interior of the preset check valve assembly;
  • FIG. 7 discloses a cross-sectional detailed view' of a normally closed check valve assembly operable to provide a high volume return flow of fluid into the high pressure cylinder during restoration of the energy dissipation and cushioning unit;
  • FIG. 8 discloses a force/stroke or energy dissipation diagram illustrating optimum energy dissipation performance of a cushioning unit
  • FIG. 9 discloses a typical force/stroke energy dissipation diagram of the type which may be exhibited by the subject invention in response to low level wave action forces imparted to a protective dock bumper;
  • FIG. 10 discloses a typical force/stroke energy dissipation diagram for normal berthing impact energies which might be occasioned under normal service conditions
  • FIG. 11 discloses a force/stroke energy dissipation diagram indicating an overload capacity capability of the subject invention which is automatically available in instances of accidental excessive velocity impact loading during a berthing operation;
  • FIG. 12 discloses a comparative force/stroke or kinetic energy dissipation diagram for the subject invention with respect to conventional bumper cushioning devices.
  • FIGS. l2A-D disclose schematic pictorial views of dock bumper units which are depicted on the kinetic energy dissipation diagram of FIG. 12.
  • FIG. 1 a typical operational environment for the subject method and apparatus for cushioning and dissipating impact forces according to a preferred embodiment of the invention. More particularly a pier is disclosed of the type which projects outwardly into a body of water 22.
  • seaward face of the pier carries a docking or mooring 4' bumper 24 to protect the pier from direct mechanical impact loading from a moored vessel 26.
  • the pier 20 may be of a variety of designs, including a shore mounted installation or an offshore berthing dolphin or the like. Still further, the pier 20 may be representative of any offshore structure which requires the protection of a docking bumper 24.
  • a floating vessel 26 such as a material tanker, barge or the like, is highly likely to damage a fixed structure during a normal berthing operation unless some form of cushioning or energy dissipation is provided.
  • the vessel 26 is moored against the pier 20, wave action tends to cyclically mudge the vessel against the relatively fixed and immobile pier. Accordingly, here again, some form of energy dissipation is required in order to minimize the possibility of damage to the pier or the hull of the contiguous vessel.
  • the docking bumper 24 is connected to the pier 20 through the provision of a system 28 of countering linkages 30. Impact energy imparted to the bumper 24 is dissipated by a plurality of generally orthogonally mounted hydraulic cushioning units 32.
  • the hydraulic cushioning units 32 comprise the subject matter of the instant invention and, as will be discussed in detail hereinafter, are operable to cushion impact loads and dissipate kinetic energy in a highly efficient manner over a wide range of impact loading conditions.
  • hydraulic cushioning units 32 have been depicted in FIG. 1 and discussed above in connection with a preferred marine protective bumper system it will be appreciated that the subject hydraulic cushioning units are not limited to a marine bumper environment and may find advantageous utilization in a plurality of diverse appations.
  • FIGS. 2-4 there will be seen detailed structural views of a hydraulic cushioning unit 32 according to a preferred embodiment of the invention.
  • the hydraulic cushioning unit includes a high pressure cylinder 34 which is comprised of a relatively thick circular side wall 36, note FIG. 4, a first end wall 38 at a restoring end of the cylinder and a second end wall 40 at a buff end of the cylinder.
  • the first and second cylinder ends are functionally designated as the restoring and buff ends in accordance with the direction of motion of a piston assembly 42, at least partially within the cylinder.
  • a piston rod 44 coaxially extends through the first end wall 38 and connects with a piston body member 46 mounted for translation and intimate wiping action along the cylindrical side walls 36 of the high pressure cylinder 34.
  • a second or distal end 48 of the piston rod 44 projects outwardly of the high pressurecylinder 34 and is preferably connected to a dock bumper member 24 in a manner to be discussed more fully hereinafter.
  • an accordian sleeve 50 is mounted between an extension collar 52 projecting outwardly of the first end wall 38 and a retaining collar 54 operably connected adjacent the bumper member 24.
  • Assembly hydraulic cylinder 34 is provided with a fluid impedance system 56 including a generally thin shell fluid-tight, low pressure, housing 58 having first and second end walls 60 and 62, respectively, for surrounding said high pressure cylinder 34 and providing
  • the piston body means 46 divides the interior of the hydraulic cylinder 34 into a first interior, buff, impedance zone 66 between-a first face 68 of the piston body 46 and thesecond end wall 40 of the cylinder 34.
  • a second interior, restoration, impedance zone 70 is defined by a second face 72 of the piston body 46 and the first or restoring end wall 38 of the cylinder 34.
  • the cylinder 34 as well as the surrounding chamber 64 is substantially filled with a fluid such that translatory motion of the piston body member 46 due to impact loading upon the distal end 48 of the piston rod assembly 42 is impeded or cushioned in order to advantageously dissipate impact energy.
  • This cushioning is facilitated by the provision of a plurality of generally radially extending and longitudinally, and energy dissipation, exponentially spaced ports 74 fashioned through the high pressure cylinder wall 36.
  • the exponential spacing of the port extends from the buff end 40 of the high pressure cylindrical wall 36 and progresses toward the restoring end 38 thereof.
  • ports 74 are shown in longitudinal alignment in FlGS. 2 and 3, such illustration is for convenience only and in actuality the ports may be circumferentially spaced, note FIG. 4, about the high pressure cylinder 36 as desired.
  • FIGS. 4 and 5 there will be seen detailed views of a preset check valve 80 of a type operable to be positioned within a plurality of the ports 74, note FIG. 4.
  • the first percent of the ports of the high pressure cylinder 36 are preferably unvalved to accommodate low level cyclic wave action forces.
  • the remaining 80 percent of the ports however are optimumly fitted with preset check valves 80. In terms of numerical values this would dictate that a first port 82 and possibly (depending upon the control design spacing) a second port 84 or more may be unvalved while the remainder of the ports 74 will be fitted with preset check valves 80 to accommodate high level full stroke impact energy dissipation.
  • the check valves 80 include a valve body 86 which is threaded on a lower end 88 thereof to be readily mounted upon the high pressure cylinder wall 36 (note FIG. 4).
  • a central port 90 extends through the base of the valve and projects upwardly to a termination point at a raised annular valve seat 92.
  • a generally inverted T-shaped valve plunger 94 is positioned within an internal cavity 96 of the valve body 86 and is biased downwardly against the valve seat 92 by the provision of a coil compression spring 98.
  • a plurality of relatively high flow passages 100 are radially fashioned through the valve body 86 and provide fluid communication between the chamber 96 and the return flow passage64.
  • Tension on the compression spring 98 is preset by an inwardly projecting cap 102 which is threadedly received within an upper portion 104 of the valve body 86. Appropriate selection of an axial dimension for the valve cap 102 serves to establish a previously determined preset condition of the valve plunger 94 against the valve seat 92.
  • valve plunger 94 is normally biased into a closed posture against the valve seat 92 thus preventing flow of fluid through the valve ports 74 within the high pressure cylinder wall 36. vln the event however sufficient fluid pressure is generated within the buff impedance zone 66 to lift the valve plunger 94, fluid will flow through the passage 90 to be metered between the valve body 94 and the annular seat 92.
  • the capacity of radially extending ports 100 is much greater then the annular orifice provided by the valve seat 92 and valve plunger 94 combination, thus regulation of flow is provided by the extent to which the valve plunger 94 is lifted by fluid pressure within the buff end of the high pressure cylinder.
  • a certain preset pressure within the high pressure cylinder 36 is necessary in order to provide an initial flow through the valve 80.
  • This pressure is typically selected as 100 percent of the design capacity of the hydraulic unit.
  • valves 80 will fully open until an upper planar surface 106 of the valve body abuts against planar surface 108 of the valve cap.
  • valve 80 serves to provide normal valved cushioning to accommodate normal im pact load occasioned against a dock bumper and also high level valved cushioning to accommodate emergency or overload capacity due to excessive berthing velocities of a floating vessel against a dock bumper.
  • isolation and Restoring System Referring particularly to FIGS. 2 and 3 there will be seen an isolation and restoring system 110 including an outer generally cylindrical wall structure 112 having a first end 1 14 extending toward the distal end 48 of the piston rod 42 and a second end 116 extending toward the second end of the hydraulic cylinder 34.
  • a generally cylindrical mounting assembly 118 is operably connected to the distal end 48 of the piston rod 42 and a similar generally cylindrical mounting assembly 120 is operably connected to the second end 40 of the hydraulic cylinder 34.
  • Generally frustroconically configured elastomeric members 122 and 124 are mounted between the ends 114 and 116 of the cylinder 112 and the mounting assemblies 118 and 120 respectively.
  • the mounting assemblies 118, frustroconical member 122, cylindrical member 112, frustroconical member 124 and mounting assembly 120 serve in combination to enhouse and encapsule in sealed isolation the interiorly positioned hydraulic cylinder assembly. Such isolation is preferably established at an assembly plant and is particularly significant when the hydraulic cushioning unit is being utilized in a generally corrosive marine environment.
  • the piston body 46 operably translates in response to impact loads through the high pressure cylinder 36 to a buff end 40 thereof. Once the unit is compressed however, note specifically FIG. 3, it is highly desirable to quickly restore the cylinder without producing an undesirable rebound force.
  • Restoration force for the subject hydraulic cushioning assembly is achieved through the flexure and shear action of the elastomeric member 122 and 124. More particularly, once impact energy is dissipated the frustroconical elastomeric members will flex to quickly restore the unit to a nominal extended posture. Rebound energy however, is not imparted to the dock bumper 24 and into a contiguously moored juxtaposed vessel.
  • the high pressure cylinder wall 36 is fitted with a unitary relatively high capacity restoring port 126 which extends through the cylinder wall 36 generally at the first or restored end of the cushioning unit. Accordingly, as the piston body 46 translates through the hydraulic cylinder toward the first or restored end, fluid will be metered through the port 126 and into the surrounding annular fluid passage 64.
  • valve 128 comprises a body 130 connected by threaded coupling means 132 to the exterior of high pressure cylinder wall 36 (note FIG. 4).
  • a valve member 134 is telescopingly mounted within valve body 130.
  • Valve member 134 is generally cylindrical in character and comprises a cylindrical side wall 136 provided with a plurality of radial ports 138.
  • An imperforate head wall 140 connected with side wall 136 provides a sealing surface 142 to sealing engage a valve seat 144 formed on valve body 130.
  • a coil spring 146 interposed between valve member carried abutment 148 and a valve body carried abuttment 150 serves to yieldably bias the valve member 134 in a closed position.
  • valve 134 In response to a relatively low pressure in annular chamber 64, subsequent to a prior buff movement, the valve 134 will automatically open so as to allow the return flow of fluid from the cavity 64 into the buff zone 66.
  • one end of the assembly is universally connected to a marine means 150 such as a dock, pier, offshore tower, or in some instances even a vessel.
  • a universal mounting assembly 152 includes a spherical ball 154 operably encapsuled within a generally spherical cavity 156 fashioned within a mounting block 158.
  • the mounting block 158 in turn is fixedly connected to a plate 160 which may be connected to the pier 150 by conventional threaded fasteners 162 or the like.
  • the other end of the mounting block 158 is fitted with a cylindrical shell 164 which in turn is weldingly connected to the mounting unit of the isolation and restoring system.
  • the other end of the hydraulic cushioning assembly is provided with a universal mounting assembly including a spherical connecting member 172 mounted at the distal end 48 of the piston rod 42 and being received within a compatibly dimensioned spherical cavity 174 fashioned within a mounting block 176.
  • the mounting block at one end is weldingly connected to a mounting plate 178 which in turn is connected to a bumper 24 through the provision of conventional threaded fasteners 180.
  • the other end of the mounting block 176 is connected to the mounting cylinder 118 of the restoring and isolation system adjacent the distal end of the piston rod.
  • FIGS. 8 through 11 there will be seen force displacements or energy performance diagrams depicting an optimum standard and various modes of actual energy dissipation operation of the subject hydraulic cushioning invention.
  • a perfect energy diagram would comprise a rectangular trace wherein 100 percent of design force levels are immediately realized with minimal stroke and such force levels are maintained in a horizontal continuous condition throughout 100 percent of the stroke whereby the input energy will have been dissipated. Once the input energy-is dissipated, the force level would fall vertically to zero and the unit would be restored with zero force utilization.
  • the area disclosed in cross-hatching within rectangle 204 represents the amount of kinetic energy absorbed by a perfect energy dissipation device.
  • FIG. 9 there will be seen a performance diagram traced in accordance with one operative mode of the subject invention wherein cyclic wave action impulses are absorbed and dissipated by the subject invention. More particularly, for very low level wave action forces, the piston body 46 will traverse a short sroke distance, possibly 20 percent or less of its designed capacity. During this first 20 percent stroke the unvalved port 82 and possibly port 84 will be utilized with the valves 80 maintained in a preset closed posture.
  • the energy dissipation trace 206 is a generally square response diagram wherein the energy is absorbed at approximately 50 percent of the design force level over 20 percent of the design stroke.
  • the restoring mechanism is operable to quickly restore the unit to a fully extended operative posture. It will be appreciated by those skilled in the art that the low level energy dissipation provided by the subject system approaches a perfect energy diagram.
  • FIG. 10 there will be seen a nominal energy performance diagram 208 for a hydraulic unit according to the subject invention wherein sufficient impact energy is occasioned so as to open the preset valves and thus dissipate energy in accordance with utilization of I percent of the nominal designed force level for the hydraulic cushioning unit. Because of a relatively low impact energy level the stroke is only 50 to 60 percent of nominal design capacity, and thus the unit will quickly restore itself to accommodate subsequent impact loads.
  • diagram 208 is substantially rectangular and thus represents a near perfect energy dissipation performance response.
  • overload energy diagram 210 wherein overload capacity is accommodated by the subject cushioning unit to accommodate excessive berthing velocities.
  • the fluid pressure in the buff impedance zone 66 reaches a magnitude to completely open the valve 94 and thus planar surface 106 will abut against the cap 108.
  • This maximum opening is designed to cushion approximately 200 percent the nominal designed capacity of the unit and all of the stroke is utilized to dissipate the kinetic energy imparted to the hydraulic cushioning unit.
  • a near perfect energy dissipation performance diagram is exhibited.
  • FIGS. 12 and l2A-D there will be seen comparative force-deflection or energy dissipation diagrams for various commercially available shock absorber assemblies for a dock bumper system as compared with an energy dissipation diagram for the subject hydraulic shock absorbing system. More particularly FIG. 12 discloses a grid with deflection in inches along the abscissa and force levels in thousands of pounds or KIPS along the ordinate.
  • a first diagram A represents the force/deflection or energy dissipation for the unit pictorially disclosed in FIG. 12A.
  • This unit comprises a generally solid elastomeric block of rubber 212 with mounting plates 214 and 216 affixed to the ends thereof.
  • Trace A is typical of the previously known elastomeric units and may be characterized as comprising a linearly sloping first segment 218 wherein the elastomeric unit 212 is deflecting and the energy absorption is gradually increasing.
  • the energy has been dissipated as at 220 and undesirable rebound force 222 is imparted by the compressed elastomeric unit back to the marine vessel or the like.
  • a second diagram B represents the force/deflection or energy dissipation performance for a cushioning unit such as depicted in FIG. 128. More particularly, this unit is comprised of a cell-type cylinderical elastomeric body 224 which is fitted at either end with mounting plates 226 and 228. Trace B is similar to trace A and may generally be characterized as being comprised of a sloping initial segment 230 and a rebound force 232.
  • a third diagram C represents energy dissipation capability for a cushioning unit such as depicted in FIG. 12C.
  • This unit includes a pair 234 and 236 of mounting assemblies and an intermediate oppositely directed assembly 238.
  • Elastomeric arms 240 and 242 connect the units 234 and 236 respectively to the intermediate member 238.
  • the performance diagram for this assembly again includes an initial sloping segment 244 coupled with a rebound force 246.
  • FIG. 12D displays a generally rectangular energy dissipation curve wherein maximum forces are realized in a very short stroke and are maintained in a generally constant level throughout the stroke until the input energy is dissipated. Once the energy is dissipated, the deflection or stroke travel terminates and the force level falls to essentially zero. The unit is then restored in a controlled yet rapid manner with negligible rebound energy.
  • the subject marine bumper hydraulic cushioning unit coinprises a significant advance in marine bumper design and exhibits to a nearly perfect kinetic energy dissipation diagram, wherein a significant amount of energy is dissipated for an initial small deflection which is maintained substantially constant until the input energy is dissipated whereupon the unit substantially ceases to travel and rapidly restores itself to a fully extended posture.
  • the subject isolation and restoring assembly of the subject invention isolates the hydraulic cushioning unit from a generally hostile marine environment while providing rapid and effective restoring capacity for the hydraulic unit.
  • Yet a further significant advantage of the invention entails the specific hydraulic cushioning unit as applied in a marine environment wherein exponential porting provides constant energy dissipation and normally preset check valve assemblies provide an inexpensive yet highly reliable performance pattern for dissipating impact energies occasioned in a marine environment.
  • Apparatus operable to be positioned between a marine means and a protective bumper me ans for dissipating energy imparted to the protective bumper means by permitting cushioned relative movement of the protective bumper means relative to the marine means, said apparatus comprising:
  • cylinder means having wall means including,
  • piston means slidably disposed within said cylinder means and including,
  • piston rod means translatably projecting through said first end wall means of said cylinder means and having a first end thereof connected to said piston body means;
  • impedance means associated with said cylinder means and said piston means for cushioning translation of said piston body means from a normal position of adjacency to said first end wall wherein said apparatus is in an extended posture operably ready to dissipate energy imparted to the protective bumper means to a position of adjacency to said second end wall wherein said apparatus is in a closed posture operably following dissipation of energy imparted to the protective bumper means;
  • An apparatus for dissipating energy as defined in claim 1 wherein said means surrounding said cylinder means for isolating and for biasing comprises:
  • annular means connected to and extending between the other end of said housing and the other of said means for operably connecting said second end wall means of said cylinder means and said means for operably connecting said second, distal, end of said piston rod means;
  • said housing means, elastomeric annulus, and said annular means being operably to enhouse said hydraulic cylinder means and said piston means for isolating said hydraulic cylinder means and said piston means from a surrounding marine environment;
  • annular means comprises:
  • said elastomeric annulus and said second elastomeric annulus being each generally frustoconically configured wherein translation of said second, distal,
  • An apparatus for dissipating energy as defined in claim 1 wherein said means for operably connected said second end wall means of said cylinder means to one of the marine means and the protective bumper means includes:
  • An apparatus for dissipating energy as defined in claim 1 wherein said impedance means comprises:
  • said at least one port means comprises: a plurality of ports radially extending through said cylinder side wall means and being longitudinally spaced from the buff end in an exponential pattern toward the restored end of said cylinder means.
  • a method for dissipating energy imparted to a marine protective bumper means with apparatus mounted between the marine bumper means and a marine means including:
  • cylinder means having wall means including,
  • piston body means translatably mounted within means, one being positioned in each of an initial plurality of said plurality of radially extending exponentially spaced ports with the remainder of the radial ports positioned nearest to the restored end of said cylinder means remaining unvalved wherein first low level buff forces tending to translate said piston body means toward the bluff end of said cylinder means will be dissipated by displacing fluid from said buff end impedance zone into said annular return flow passage through said radial ports popiston rod means translatably projecting through said first end wall means of said cylinder means andhaving a first end thereof connected to said piston body means; the steps of said method comprising:
  • said at least another port means comprises a relatively high capacity unitary port radially extending cushioning relatively higher level impact forces imparted against the marine protective bumper means by, unseating a plurality of normally closed preset valve means covering at least some of a plurality of radially directed port means fashioned through said cylinder wall means between the first face of said piston body means and said second end wall means, said plurality of ports being first end wall means, and
  • piston means slidably disposed within said cylinder means and including,
  • piston rod means translatably projecting through said first end wall means of said cylinder means exponentially spaced from said second end wall 10 and having a first end thereof connected to said toward first face of said piston body, and piston body means; metering fluid through said plurality of unseated the steps of said method comprising:

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Ocean & Marine Engineering (AREA)
  • Environmental & Geological Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Damping Devices (AREA)
US453980A 1974-03-22 1974-03-22 Sealed cushioning unit Expired - Lifetime US3864922A (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
US453980A US3864922A (en) 1974-03-22 1974-03-22 Sealed cushioning unit
US05/538,803 US4043545A (en) 1974-03-22 1975-01-06 Sealed cushioning unit
JP3287475A JPS5526246B2 (2) 1974-03-22 1975-03-18
DE19752548410 DE2548410C3 (de) 1974-03-22 1975-03-19 Hydraulische Stoßdämpfungsvorrichtung
DE19752511965 DE2511965A1 (de) 1974-03-22 1975-03-19 Daempfungsvorrichtung zum abstuetzen eines prellbocks an einer pier o.dgl.
FR7508931A FR2274738A1 (fr) 1974-03-22 1975-03-21 Dispositif et procede de dissipation d'energie
IT21529/75A IT1034494B (it) 1974-03-22 1975-03-21 Gruppo ammortizzatore a tenta
GB12010/75A GB1500074A (en) 1974-03-22 1975-03-21 Hydraulic cushioning unit

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US453980A US3864922A (en) 1974-03-22 1974-03-22 Sealed cushioning unit

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US05/538,803 Division US4043545A (en) 1974-03-22 1975-01-06 Sealed cushioning unit

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US3864922A true US3864922A (en) 1975-02-11

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US453980A Expired - Lifetime US3864922A (en) 1974-03-22 1974-03-22 Sealed cushioning unit

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US (1) US3864922A (2)
JP (1) JPS5526246B2 (2)
DE (1) DE2511965A1 (2)
FR (1) FR2274738A1 (2)
GB (1) GB1500074A (2)
IT (1) IT1034494B (2)

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3974794A (en) * 1973-11-06 1976-08-17 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Vacuum actuated ship mooring devices
US3981114A (en) * 1975-06-13 1976-09-21 General Motors Corporation Energy absorbing permanently deformable collapsible column
JPS527591A (en) * 1975-07-08 1977-01-20 Oiles Ind Co Ltd Means for protecting ship side
US4026533A (en) * 1975-08-29 1977-05-31 Hennells Ransom J Shock absorber with conical control elements
US4032126A (en) * 1976-03-29 1977-06-28 Laughlin William N Shock absorbing apparatus
US4039176A (en) * 1975-08-04 1977-08-02 Vetco Offshore Industries, Inc. Marine riser spider shock absorber apparatus
US4084801A (en) * 1975-11-28 1978-04-18 Oil States Rubber Company Shock energy absorbing multi-segment load cell
US4109474A (en) * 1976-10-15 1978-08-29 Regal Tool & Rubber Co., Inc. Bumper assembly shock cell system
US4137861A (en) * 1974-06-26 1979-02-06 Irving Brummenaes Process for mooring a ship and a fender arrangement for such mooring process
US4192045A (en) * 1978-03-20 1980-03-11 Samcoe Holding Corporation Adjustable spreader for tubular knitted fabric
US4273473A (en) * 1979-03-13 1981-06-16 Regal Tool & Rubber Co., Inc. Shock absorbing column
US4305185A (en) * 1978-03-20 1981-12-15 Samcoe Holding Corporation Adjustable spreader for tubular knitted fabric
US4337009A (en) * 1979-07-27 1982-06-29 Regal International, Inc. Marine landing structure with omni directional energy absorbing characteristics
US4345537A (en) * 1977-12-26 1982-08-24 Bridgestone Tire Company Limited Apparatus for restraining and berthing a floating body
US4399764A (en) * 1981-07-06 1983-08-23 The United States Of America As Represented By The Secretary Of The Navy Passive shock mitigation system with sea water metering shock absorber
US4773349A (en) * 1987-12-07 1988-09-27 Mckinney Ronald W Boat dock bumper
US5415303A (en) * 1993-08-27 1995-05-16 F M Industries, Inc. Railcar cushion unit
US5487480A (en) * 1993-06-10 1996-01-30 Oleo International Holdings Limited Hydro-pneumatic cushioning device
US6168143B1 (en) * 1996-05-07 2001-01-02 Phoenix Aktiengesellschaft Pneumatic spring
WO2003055740A1 (en) * 2002-01-03 2003-07-10 Mooring Systems Limited Ship-based mooring device
US20060243185A1 (en) * 2005-04-27 2006-11-02 Derochers Paul P Retractable bumper system and method
US20100287715A1 (en) * 2009-03-25 2010-11-18 Voyiadjis George Z Fenders for Pier Protection Against Vessel Collision
US8087371B1 (en) * 2009-09-25 2012-01-03 The United States Of America As Represented By The Secretary Of The Navy Deployable and inflatable fendering apparatus and method
US10760598B2 (en) 2017-09-01 2020-09-01 Enerpac Tool Group Corp. Hybrid spring for a hydraulic cylinder
CN112937793A (zh) * 2021-03-31 2021-06-11 山东交通学院 一种应用于船舶的安全防护装置
US20220297807A1 (en) * 2016-01-08 2022-09-22 Northern Offshore Services Ab Fender arrangement for docking a marine vessel with a boat landing of a marine off-shore structure
CN116658567A (zh) * 2023-04-14 2023-08-29 中北大学 一种高速冲击保护装置

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US4560150A (en) * 1983-11-25 1985-12-24 Imperial Clevite Inc. Dry viscous spring strut
GB2165334B (en) * 1984-10-08 1988-10-12 Giken Kogyo Kk Impact energy absorbing device for waterway walls
US6736420B2 (en) 2000-03-03 2004-05-18 Jost International Corporation Carrier assembly for a fifth wheel
CN112693574B (zh) * 2021-01-21 2022-05-17 上海交通大学 一种基于非牛顿流体的甲板对接单元缓冲装置

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US3109404A (en) * 1961-07-20 1963-11-05 Cleveland Pneumatic Ind Inc Marine fenders
US3301410A (en) * 1966-02-14 1967-01-31 Halliburton Co Hydraulic shock absorbing apparatus
US3791534A (en) * 1968-08-14 1974-02-12 Halliburton Co Valve apparatus for controlling train action

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Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3974794A (en) * 1973-11-06 1976-08-17 Ishikawajima-Harima Jukogyo Kabushiki Kaisha Vacuum actuated ship mooring devices
US4137861A (en) * 1974-06-26 1979-02-06 Irving Brummenaes Process for mooring a ship and a fender arrangement for such mooring process
US3981114A (en) * 1975-06-13 1976-09-21 General Motors Corporation Energy absorbing permanently deformable collapsible column
JPS527591A (en) * 1975-07-08 1977-01-20 Oiles Ind Co Ltd Means for protecting ship side
US4039176A (en) * 1975-08-04 1977-08-02 Vetco Offshore Industries, Inc. Marine riser spider shock absorber apparatus
US4026533A (en) * 1975-08-29 1977-05-31 Hennells Ransom J Shock absorber with conical control elements
US4084801A (en) * 1975-11-28 1978-04-18 Oil States Rubber Company Shock energy absorbing multi-segment load cell
US4032126A (en) * 1976-03-29 1977-06-28 Laughlin William N Shock absorbing apparatus
US4109474A (en) * 1976-10-15 1978-08-29 Regal Tool & Rubber Co., Inc. Bumper assembly shock cell system
US4345537A (en) * 1977-12-26 1982-08-24 Bridgestone Tire Company Limited Apparatus for restraining and berthing a floating body
US4192045A (en) * 1978-03-20 1980-03-11 Samcoe Holding Corporation Adjustable spreader for tubular knitted fabric
US4305185A (en) * 1978-03-20 1981-12-15 Samcoe Holding Corporation Adjustable spreader for tubular knitted fabric
US4273473A (en) * 1979-03-13 1981-06-16 Regal Tool & Rubber Co., Inc. Shock absorbing column
US4337009A (en) * 1979-07-27 1982-06-29 Regal International, Inc. Marine landing structure with omni directional energy absorbing characteristics
US4399764A (en) * 1981-07-06 1983-08-23 The United States Of America As Represented By The Secretary Of The Navy Passive shock mitigation system with sea water metering shock absorber
US4773349A (en) * 1987-12-07 1988-09-27 Mckinney Ronald W Boat dock bumper
US5487480A (en) * 1993-06-10 1996-01-30 Oleo International Holdings Limited Hydro-pneumatic cushioning device
US5415303A (en) * 1993-08-27 1995-05-16 F M Industries, Inc. Railcar cushion unit
US6168143B1 (en) * 1996-05-07 2001-01-02 Phoenix Aktiengesellschaft Pneumatic spring
WO2003055740A1 (en) * 2002-01-03 2003-07-10 Mooring Systems Limited Ship-based mooring device
US7159526B2 (en) * 2005-04-27 2007-01-09 Derochers Paul P Retractable bumper system and method
US20060243185A1 (en) * 2005-04-27 2006-11-02 Derochers Paul P Retractable bumper system and method
US20100287715A1 (en) * 2009-03-25 2010-11-18 Voyiadjis George Z Fenders for Pier Protection Against Vessel Collision
US8484787B2 (en) * 2009-03-25 2013-07-16 Board Of Supervisors Of Louisiana State University And Agricultural And Mechanics College Fenders for pier protection against vessel collision
US8087371B1 (en) * 2009-09-25 2012-01-03 The United States Of America As Represented By The Secretary Of The Navy Deployable and inflatable fendering apparatus and method
US20220297807A1 (en) * 2016-01-08 2022-09-22 Northern Offshore Services Ab Fender arrangement for docking a marine vessel with a boat landing of a marine off-shore structure
US12116090B2 (en) * 2016-01-08 2024-10-15 Northern Offshore Services Ab Fender arrangement for docking a marine vessel with a boat landing of a marine off-shore structure
US10760598B2 (en) 2017-09-01 2020-09-01 Enerpac Tool Group Corp. Hybrid spring for a hydraulic cylinder
CN112937793A (zh) * 2021-03-31 2021-06-11 山东交通学院 一种应用于船舶的安全防护装置
CN116658567A (zh) * 2023-04-14 2023-08-29 中北大学 一种高速冲击保护装置

Also Published As

Publication number Publication date
GB1500074A (en) 1978-02-08
FR2274738B3 (2) 1977-11-25
IT1034494B (it) 1979-09-10
DE2548410A1 (de) 1976-05-06
FR2274738A1 (fr) 1976-01-09
DE2511965A1 (de) 1975-09-25
JPS5526246B2 (2) 1980-07-11
JPS50127388A (2) 1975-10-07
DE2548410B2 (de) 1976-12-23

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