WO2000047909A1 - A compact, resistance regulated, multiple output hydraulic package and seal valve arrangement - Google Patents
A compact, resistance regulated, multiple output hydraulic package and seal valve arrangement Download PDFInfo
- Publication number
- WO2000047909A1 WO2000047909A1 PCT/US1999/029347 US9929347W WO0047909A1 WO 2000047909 A1 WO2000047909 A1 WO 2000047909A1 US 9929347 W US9929347 W US 9929347W WO 0047909 A1 WO0047909 A1 WO 0047909A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- chamber
- piston
- fluid
- passage
- ram
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1433—End caps
-
- 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
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
-
- 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
- F15B15/149—Fluid interconnections, e.g. fluid connectors, passages
-
- 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
- F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7734—Fluid opened valve requiring reset
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7771—Bi-directional flow valves
-
- 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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7904—Reciprocating valves
- Y10T137/7905—Plural biasing means
Definitions
- the present invention relates to manually actuated, hydraulically operated tools of the type having working elements such as jaws or cutters which close over a workpiece. More particularly, the invention relates to a hand tool having a hydraulic circuit contained entirely within a housing containing two pistons. One piston converts manual input force to fluid pressure. The other piston converts fluid pressure to output force for imposing on the work. The tool enables three speeds of closure of jaw or corresponding tool movement at one input speed.
- the field of endeavor most likely to benefit from this invention is the construction industry in that the device is specifically intended for use in creating effective hand tools which are often used in the building trades.
- the general fields of mechanical assembly and automotive repair could also benefit from the apparatus herein disclosed.
- any process requiring crimping, bending, punching, cutting, pressing, etc. could significantly benefit from the performance characteristics of the instant hydraulic tool.
- An object of the present invention is to fulfill the needs referred to above.
- this objective is obtained by providing a hydraulic device including a housing.
- a bulkhead is disposed in the housing.
- a pump piston is provided in the housing and has first and second end surfaces with the second end surface of the pump piston and surfaces of the housing and of the bulkhead defining a pumping chamber.
- the pump piston is constructed and arranged to move within the housing to develop pressure on fluid in the pumping chamber.
- the first end surface of the pump piston and surfaces of the housing define a pump reservoir chamber.
- a ram piston is provided in the housing and has first and second end surfaces with the first end surface of the ram piston and surfaces of the housing and of the bulkhead defining a drive chamber.
- Connecting structure is associated with the bulkhead to communicate the pumping chamber with the drive chamber so that fluid pressure developed in the pumping chamber may be exerted on the first end surface of said ram piston.
- a barrier is provided in the housing between an end of the housing and the ram piston. Surfaces of the housing, the barrier and the second end surface of the ram piston define a ram reservoir chamber, and surfaces of the second end of the housing and of the barrier define an accumulator chamber. Passage and valve structure is associated with the barrier to selectively permit fluid to flow from the ram reservoir chamber to the accumulator chamber and from the accumulator chamber to the ram reservoir chamber. Passage and valve structure is associated with the ram piston to permit fluid flow from the ram reservoir chamber to the drive chamber.
- Passage and valve structure is associated with the pump piston to selectively permit fluid flow from the pump reservoir chamber to the pumping chamber and from the pumping chamber to the pump reservoir chamber.
- Communication structure fluidly communicates the accumulator chamber with the pump reservoir chamber.
- the communication structure, the connecting structure and the passage and valve structures are constructed and arranged to permit movement of the ram piston selectively at three speeds with corresponding magnitudes of force relative to a single speed of the pump piston.
- a hydraulic tool in accordance with another aspect of the invention, includes a housing.
- a pump piston is disposed in the housing to define a pumping chamber at one end thereof and a pump reservoir chamber at another end of the pump piston.
- the pump piston is constructed and arranged to move within the housing to develop pressure on fluid in the pumping chamber.
- a ram piston is disposed in the housing to define a drive chamber.
- Fluid circuitry permits fluid communication between the pumping chamber and the drive chamber such that fluid pressure developed in the pumping chamber is imposed on the ram piston to move the ram piston in a certain direction.
- the fluid circuitry is constructed and arranged to move the ram piston in the certain direction at three different speeds with corresponding magnitudes of force relative to a single speed of the pump piston.
- a ram piston return valve structure is constructed and arranged to selectively communicate the drive chamber with the pump reservoir chamber thereby initiating movement of the ram piston in a direction opposite the certain direction.
- FIG. 1 is a diagrammatic, side cross-sectional view of a hydraulic device provided in accordance with the principles of a first embodiment of the present invention
- FIG. 2 is a diagrammatic, side cross-sectional view of a hydraulic tool provided in accordance with the principles of a second embodiment of the present invention
- FIG. 3 is an enlarged view of a floating seal valve assembly associated with the barrier of the hydraulic tool of FIG. 2;
- FIG. 4 is an enlarged view of a spring retainer member of the floating seal valve assembly of FIG. 3;
- FIG. 5 is an enlarged view of the pump piston and bulkhead of the hydraulic tool of FIG. 2;
- FIG. 6 is a floating seal valve provided in accordance with another embodiment of the invention.
- a three-speed hydraulic device preferably in the form of a tool is shown, generally indicated at 10, provided in accordance with the principles of the present invention.
- the hydraulic tool 10 includes a cylindrical bulkhead 12 disposed within an interior bore 14 of a unitary cylindrical housing structure 16. Interior bore 14 encloses a ram piston 18 driven by pressurized fluid and a pump piston 20 for developing this pressure.
- a removable housing end cap 22 and 24, respectively, is provided at a first end 15 and a second end 17 of the housing 16.
- the end caps are shown as being threaded into the housing 16 but other forms of attachment, such as bolts or the like, could be used.
- the end caps 22 and 24 may be considered to be part of the housing 16.
- the cylindrical housing, piston, and ram could be of square, hexagonal or other cross-section if desired.
- the housing structure 16 may be composed of separate housings, such as, a pump housing and a ram housing.
- interior bore 14 is subdivided into a pumping chamber D, a driving chamber C, a pump reservoir chamber E, a ram reservoir chamber B and an accumulator chamber A.
- the chambers A, B and E receive and dispense fluid displaced during operation of the tool 10.
- the pumping chamber is defined by a first end surface 25 of the pump piston 20 and surfaces of the bulkhead 12 and of the housing 16.
- Pump reservoir chamber E is defined by the surfaces of the first end 15 of the housing 16 and a second end surface 27 of the pump piston 20.
- the drive chamber C is defined by surfaces of the bulkhead 12 and of the housing 16 and a first or rear surface 72 of the ram piston 18.
- Ram reservoir chamber B is defined by surfaces of the housing 16, of surface 73 of the barrier 22, and of a second or front surface 74 of the ram piston 18. Finally, accumulator chamber A is defined by surfaces of the housing 16, of surface 75 of the barrier 22, and of surface 77 of an accumulator piston 30 which is located at the second end of the housing 16.
- the total volume of all the chambers is slightly variable due to fluid displaced by the pump piston rod 26 and the ram piston rod 28 during movement of the pump piston 20 and ram piston 18.
- This rod displacement volume variation is accommodated by a spring loaded accumulator piston 30, which forms a movable end wall sealing chamber A at the left side thereof, as depicted in FIG. 1.
- Accumulator piston 30 has an opening closely cooperating with ram piston rod 28.
- a spring 32 urges the accumulator piston 30 to the right as show in FIG. 1.
- Spring 32 is suitably entrapped within housing 16 so that it acts continuously against piston 30.
- the accumulator piston 30 may be considered part of the second end of the housing 16.
- the area within housing 16 enclosing spring 32 is open to the atmosphere via ports 34 to avoid fluid pressures below atmospheric pressure, which would tend to interfere with operation of the tool 10.
- the bulkhead 12 includes a ram piston return and overpressure valve structure, generally indicated at 36 in FIG. 1.
- the valve structure 36 is preferably a spring loaded valve having a spring 38 which acts on valve member 40 to seal opening 42 in the bulkhead 12. Opening 42 communicates with drive chamber C and with chamber 43 which houses the valve structure 36.
- a conduit 44 is operatively coupled with the valve member 40 at one end thereof. The other end of the conduit 44 is operatively associated with the pump piston 20 and communicates with pump reservoir chamber E through check valve 46.
- conduit 50 are provided about the conduit 44 to permit the normal pump stroke without moving the conduit 44 or the valve structure 36.
- a conduit 52 is in communication with chamber 43 and communicates with an external conduit 54.
- Conduit 54 is in communication with accumulator chamber A and together with conduit 52, chamber 43, conduit 44 define communication structure fluidly communicating the accumulator chamber A with the pump reservoir chamber E.
- Check valve 46 may be considered to be part of the communication structure.
- conduit 54 is shown to be external to the housing 16, it can be appreciated that the conduit 54 may be a channel defined in the wall of housing 16.
- configuration of the communication structure is not limited to that described above, but includes any structure which permits fluid communication from the accumulator chamber A to pump reservoir chamber E.
- a first mode of operation of the tool 10 is a high-speed, low force mode in which jaws (not shown) or other working elements associated with the hydraulic tool 10 are moved into engagement with a workpiece. There is little need for force beyond moving the working elements to the point of contact with the work piece. Hence, force is exchanged for increase speed of closure of the jaws during positioning of the tool on the workpiece.
- the connecting structure comprises conduits 58 and 60, and an annular channel 62 so as to fluidly communicate chambers C and D.
- a filter 66 is provided in channel 62 to filter out any foreign material in the fluid so as to not disrupt operation of any of the valves in the tool 10.
- pumping chamber D communicates with drive chamber C through conduit 58, 60 and channel 62 via valve structure 64 and ram reservoir chamber B communicates with the accumulator chamber A through conduit 76 via valve structure 78. It can be appreciated that for a given force applied to piston rod 26 in the low speed, high force mode, the pressure generated in pumping chamber D increases in proportion to the decrease in the net effective area of piston 20. This increased pressure is translated to ram piston 18 which in turn delivers an increased force to the ram rod 28.
- the valve structure 36 functions as a combined over-pressure relief and pressure release mechanism.
- fluid pressure in the tool 10 continues to increase by action of the pump piston 20 which in turn imparts increased force on ram piston 28.
- valve 40 disengages form its seat, thus permitting fluid flow through opening 42.
- Fluid moves into bulkhead chamber 43 until the pressure in the drive chamber C returns to the pre-determined maximum pressure.
- Fluid entering chamber 43 is distributed to piston reservoir chamber E through conduit 44 and secondarily through conduits 52, 54 and into chamber A.
- This overpressure relief mechanism prevents the tool 10 from becoming too aggressive for its work and provides the user a cautionary measure of safety.
- valve member 40 When valve member 40 is opened, fluid in the drive chamber C communicates with the pump reservoir chamber E via conduit 44 and fluid in the pump reservoir chamber E communicates with the pumping chamber D via passage passages 86. Fluid demands for chambers D and E have essentially already been supplied, accumulator chamber A now expands to take up the fluid displaced by the ram rod 28 as it is retracted into the tool 10. .
- the ram piston 18 moves at increased speed and reduced force relative to the pump piston 20 when fluid is routed from one side of the ram piston 18 to the other side thereof.
- ram piston 18 moves at a reduced speed and with increased force relative to the pump piston 20 when fluid is routed from one side of the pump piston 20 to the other side thereof.
- check valves described herein are conventional and preferably of the spring- actuated, ball or needle valve type.
- the floating seal valve assembly includes a first floating seal valve, generally indicated at 113, comprising an O-ring 115 sealing a passage 131 between an outer periphery of the generally cylindrical barrier 122 and the annular wall defining inner bore 114 of the housing 116, and a spring retainer member 117 coupled to face 119 of the barrier 122 and operatively associated with the O-ring 115.
- the floating seal valve 113 also includes a glide member 111 provided between the O-ring 115 and retainer member 117. The spring retainer member 117 slides the glide member 111 on the bore 114 and holds it against a stepped shoulder 134 defined in the barrier 122.
- the spring load of retainer member 125 is selected such that when conditions are such that fluid may flow from ram reservoir chamber B to accumulator chamber A, the retainer 125 will flex to permit fluid to flow past the O-ring 123 and through passages 131 and 141 in the direction of arrow J.
- the spring load of the retainer member 117 is such that in a ram piston retracting mode, fluid may flow past O-ring 115 through passages 141 and 133 in the direction opposite to arrow J such that fluid in the accumulator chamber A may move into ram reservoir chamber B.
- the glide member 124 may be omitted.
- Floating seal valve structure 127 including O-ring 129, glide member 126 and spring retainer member 135, is provided at the ram piston 112.
- the retainer member 135 biases the O-ring 129 against a shoulder to seal a passage 137 between the periphery of the ram piston 112 and the housing inner bore 14.
- retainer member 135 is constructed and arranged to prevent fluid communication between the drive chamber C and ram reservoir chamber B and when required, permit large volumetric flow from ram reservoir chamber B to drive chamber C.
- the spring load of floating seal valve 121 is greater than that of floating seal valve 127 so as to effect the shift between the high-speed/low force and the mid- speed/mid force modes of operation.
- the glide member 126 may be omitted.
- the spring retainer member 117 preferably has a plurality of fingers 180 extending from a central portion 182 thereof as shown in FIG. 4.
- Spring retainer member 135 is configured similarly.
- the pump piston 120 of the second embodiment has a different valve structure associated therewith than in the first embodiment of the invention.
- FIG. 5 an enlarged view of the generally cylindrical pump piston 120 of FIG. 2 is shown.
- valve structure in form of a bi-stable floating seal valve arrangement is provided.
- the floating seal valve arrangement 132 comprises an O-ring 160 positioned to seat on a raised ridge 161 of the pump piston 120.
- Two opposing spring loaded guide rings, 162 and 164 keep the O-ring 160 on the ridge 161 and in a sealed position. Stop surfaces 163 limit the movement of the guide rings toward the O-ring 160.
- the embodiment of FIG. 2 includes a handle structure, generally indicated at 150, which is operatively associated with pump rod 26 of the pump piston to actuate the same.
- the handle structure 150 includes a hand-operated trigger member 152 which, when actuated or squeezed, causes actuation of the tool 100 and which, when released, causes the return stroke of the ram piston 112, thus resetting the tool 100. It can be appreciated that the handle structure 150 can be provided on the tool 10 of the embodiment of FIG. 1 as well.
- a mechanical linkage is coupled with the overpressure release valve structure 36 and is used to move the valve member 40 of the valve structure 36 to an open position so that fluid may flow from the drive chamber C to the accumulator chamber A and to the pump reservoir chamber E, as noted above.
- the mechanical linkage is connected to the pump piston 120 with a limited slip connection so that over travel of the pump piston 120 beyond a the normal stoke moves the valve member 40 to the opened position.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
- Valve Device For Special Equipments (AREA)
- Actuator (AREA)
- Regulating Braking Force (AREA)
- Check Valves (AREA)
- Servomotors (AREA)
- Portable Nailing Machines And Staplers (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU21738/00A AU2173800A (en) | 1999-02-09 | 1999-12-10 | A compact, resistance regulated, multiple output hydraulic package and seal valve arrangement |
EP99966118A EP1153224B1 (en) | 1999-02-09 | 1999-12-10 | A compact, resistance regulated, multiple output hydraulic package and seal valve arrangement |
DE69937501T DE69937501T2 (en) | 1999-02-09 | 1999-12-10 | COMPACT, RESISTOR-CONTROLLED MULTI-OUTPUT HYDRAULIC UNIT AND SEALING VALVE |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/246,847 US6035634A (en) | 1999-02-09 | 1999-02-09 | Compact, resistance regulated, multiple output hydraulic tool and seal valve arrangement |
US09/246,847 | 1999-02-09 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000047909A1 true WO2000047909A1 (en) | 2000-08-17 |
Family
ID=22932486
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US1999/029347 WO2000047909A1 (en) | 1999-02-09 | 1999-12-10 | A compact, resistance regulated, multiple output hydraulic package and seal valve arrangement |
Country Status (7)
Country | Link |
---|---|
US (2) | US6035634A (en) |
EP (2) | EP1153224B1 (en) |
AT (1) | ATE377718T1 (en) |
AU (1) | AU2173800A (en) |
DE (1) | DE69937501T2 (en) |
ES (1) | ES2293746T3 (en) |
WO (1) | WO2000047909A1 (en) |
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FR2974406A1 (en) * | 2011-04-21 | 2012-10-26 | Patrick Marcel Strzyzewski | AIR CONDITIONING, WATER PRODUCTION, COOLING NUCLEAR POWER PLANTS BY CONDENSATION AND THERMAL CHOKE, HYDRAULIC ENGINE HEATING BY PLATE RADIATORS AND COLUMN IN SPIRALS AND CHICANES |
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CN106715076B (en) * | 2014-08-11 | 2020-03-13 | 圣万提注塑工业(苏州)有限公司 | Actuating device and method capable of achieving multiple piston speeds |
US9993953B2 (en) | 2014-12-11 | 2018-06-12 | Syneventive Molding Solutions, Inc. | Actuator apparatus and method enabling multiple piston velocities |
DE102015118839B4 (en) | 2015-11-03 | 2017-06-01 | Tkr Spezialwerkzeuge Gmbh | Hydraulic unit for a mobile hydraulic tool |
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DE19706919C1 (en) | 1997-02-20 | 1998-10-01 | Stabilus Gmbh | Piston and cylinder unit with shut=off valve |
-
1999
- 1999-02-09 US US09/246,847 patent/US6035634A/en not_active Expired - Fee Related
- 1999-12-10 AU AU21738/00A patent/AU2173800A/en not_active Abandoned
- 1999-12-10 EP EP99966118A patent/EP1153224B1/en not_active Expired - Lifetime
- 1999-12-10 WO PCT/US1999/029347 patent/WO2000047909A1/en active IP Right Grant
- 1999-12-10 ES ES99966118T patent/ES2293746T3/en not_active Expired - Lifetime
- 1999-12-10 AT AT99966118T patent/ATE377718T1/en not_active IP Right Cessation
- 1999-12-10 EP EP07008270A patent/EP1867887A1/en not_active Withdrawn
- 1999-12-10 DE DE69937501T patent/DE69937501T2/en not_active Expired - Fee Related
- 1999-12-27 US US09/472,241 patent/US6341621B1/en not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3169455A (en) * | 1961-11-30 | 1965-02-16 | Teves Kg Alfred | Piston-and-cylinder arrangement |
US4031619A (en) * | 1976-01-19 | 1977-06-28 | Gregory Jack T | Manual, hydraulically operated tool |
US4722507A (en) * | 1985-09-25 | 1988-02-02 | Masoneilan International, Inc. | Piston sealing ring apparatus |
Also Published As
Publication number | Publication date |
---|---|
ATE377718T1 (en) | 2007-11-15 |
DE69937501T2 (en) | 2008-07-24 |
US6035634A (en) | 2000-03-14 |
EP1867887A1 (en) | 2007-12-19 |
DE69937501D1 (en) | 2007-12-20 |
EP1153224A4 (en) | 2006-02-15 |
AU2173800A (en) | 2000-08-29 |
EP1153224B1 (en) | 2007-11-07 |
EP1153224A1 (en) | 2001-11-14 |
US6341621B1 (en) | 2002-01-29 |
ES2293746T3 (en) | 2008-03-16 |
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