US3186169A - Hydraulically-operated reciprocating apparatus - Google Patents

Hydraulically-operated reciprocating apparatus Download PDF

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Publication number
US3186169A
US3186169A US322652A US32265263A US3186169A US 3186169 A US3186169 A US 3186169A US 322652 A US322652 A US 322652A US 32265263 A US32265263 A US 32265263A US 3186169 A US3186169 A US 3186169A
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United States
Prior art keywords
working
chamber
cylinder
piston
sectional area
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US322652A
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English (en)
Inventor
Hanser Johannes Ulrich
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Keelavite Hydraulics Ltd
Commercial Shearing Inc
Original Assignee
Keelavite Hydraulics Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
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Publication of US3186169A publication Critical patent/US3186169A/en
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Assigned to COMMERCIAL SHEARING INC.; A CORP OF OH. reassignment COMMERCIAL SHEARING INC.; A CORP OF OH. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SMEC SYSTEMS LIMITED
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/08—Distributing valve-gear peculiar thereto
    • F03C1/10—Distributing valve-gear peculiar thereto actuated by piston or piston-rod
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L21/00—Use of working pistons or pistons-rods as fluid-distributing valves or as valve-supporting elements, e.g. in free-piston machines
    • F01L21/02—Piston or piston-rod used as valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06—Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/007—Reciprocating-piston liquid engines with single cylinder, double-acting piston
    • F03C1/0073—Reciprocating-piston liquid engines with single cylinder, double-acting piston one side of the double-acting piston being always under the influence of the liquid under pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/08—Distributing valve-gear peculiar thereto
    • F03C1/20—Distributing valve-gear peculiar thereto specially adapted for engines generating vibration only

Definitions

  • This invention relates to hydraulically operated reciprocating apparatus of the kind comprising a double-acting working piston and cylinder assembly, providing two working chambers, the pressures in which respectively act on the piston in opposite directions relative reciprocation between the working piston and cylinder being caused by the operation of control valve apparatus which controls the supply of working liquid under pressure to and the escape of working liquid from at least one of said working chambers so as to vary the relationship between the pressures respectively in the two working chambers.
  • An object of the invention is to provide a form of hydraulically operated reciprocating apparatus of the kind in question in which one of the two working chambers has a substantially smaller cross sectional area than the other and wherein the effective circumferential length f the leakage path from said working chamber represented by the working clearances between the relatively reciprocating parts which co-operate to form the chamber will be small as compared with known constructions.
  • Hydraulically operated reciprocating apparatus of the kind referred to according to the present invention comprises a main working piston and cylinder assembly including a main working cylinder and a main working piston having a part of larger diameter disposed for reciprocation Within the main working cylinder and co-operating therewith to form a irst working chamber of larger cross sectional area, a subsidiary working piston and cylinder assembly comprising a subsidiary working piston and a subsidiary working cylinder arranged for reciprocation relatively to one another, one of such relatively moving parts being rigid with the main working piston while the other is rigid with the main working cylinder, the subsidiary working cylinder opening into the end of the main working cylinder remote from the said working chamber of larger cross-sectional area and being of smaller cross-sectional area than said working chamber of larger cross-sectional area, uid pressure means comprising at least one source of fluid pressure, passage means connecting said iiuid pressure means continuously to said working chamber of smaller cross-sectional area, relief passage means, and valve means operating to connect said working chamber of larger cross-sectional area alternate
  • FIGURE 1 is a sectional side elevation of the apparatus as a whole with the working piston in one end position
  • FIGURE 2 is a similar view to FIGURE 1 on an enlarged scale showing only the working piston and cylinder assembly showing the working piston in its other end position.
  • the apparatus comprises a main working piston and cylinder assembly including a main working cylinder 1 containing a main working piston 2 arranged to reciprocate therein and having formed thereon three lands, 3, 4 and 5, making sliding engagement with the cylinder 1 while a projection '6 extends through a cylindrical bore of smaller diameter than the lands 3, 4 and 5 to constitute a part by which a percussive tool can be actuated.
  • the arrangement thus provides an annular working chamber 7 constituting a working chamber 0f larger cross-sectional area, the pressure in which urges the working piston 2 to the right.
  • the working chamber of smaller crosssectional area the pressure in which urges the Working piston 2 to the left, is in the form of a cylinder 8 formed in a part of the working piston 2 as shown and having extending into it a tubular piston 9 which, with the cylinder 8, constitutes a subsidiary piston and cylinder assembly providing the working chamber of smaller cross-sectional area 8.
  • Opening into the working chamber 7 of larger crosssectional area is a combined inlet and outlet port 10 communicating with a port 11 in the wall of a valve chamber 12 containing a reciprocating valve 13 constituting a control valve by which the port 11 can be connected alternately to a source of iluid pressure, hereinafter described, by way of a working liquid delivery passage 14 and to a relief passage 15.
  • the end of the Working cylinder 1 remote from the Working chamber 7 is connected through a further relief passage 16 and a non-return valve 17 to the relief passage 15, While a port 18 in the main working cylinder 1 is connected by a passage 19 to the relief passage 15, and ports 20 and 21 in the main working cylinder 1 are connected respectively to pressure chambers 22 and 23 at the ends of the valve chamber 12.
  • the fluid pressure apparatus providing working liquid under pressure for causing reciprocation of the working piston 2 in the cylinder 1 comprises a continuously driven pump 24 arranged to draw liquid from a reservoir 25 and deliver it to the working liquid delivery passage 14, a return flow passage with a pressure relief valve 26 therein being provided to permit escape of surplus liquid from the delivery passage 14 via the passage 15 back to the reservoir 25, while maintaining a predetermined pressure within the delivery passage 14.
  • the delivery passage 14 also communicates with the liquid pressure chamber 27 of a rst hydraulic accumulator device 28 of the well-known gas-loaded -type into and out of which hydraulic accumulator working liquid can therefore flow respectively during the periods when the supply of working liquid to the port 11 via the valve 13 is interrupted and during the periods when such ow is taking place.
  • liquid ychamber of a further hydraulic accumulator 30 also ⁇ of the gas-loaded type and having a piston 31 dividing the :liquid chamber from the gas chamber 32 in which a predetermined mean gas pressure can be established.
  • the liquid cham-ber of the hydraulic .accumulator 30 communicates continuously and directly by way lof an Iopenpassage 33 with the cylinder 8 which constitutes the subsidiary Workin-g chamber.
  • FIGURE .1 the main working piston 2 is shown at the right hand end .of its travel, while the valve 13 occupies the position into which it will just have moved due to the working piston having reached such end of its travel, and FIGURE 2 shows the working piston at the 3 left hand end of its travel.
  • Liquid is maintained under pressure at all times during operation in the liquid chamber of the accumulator ⁇ 39 by the pu-mp 24 via the non-return valve 29 and the pressure in such pressure chamber .will be increased .as the working piston 2 moves to the right, and liquid is thus displaced from the chamber 8 into the accumulator since the non-return valve 29 prevents such displaced liquid tbeing returned to the delivery -passage 14.
  • the capacity and dimensions of the accumulator 30 are such in relation to the stroke of the piston 2 and the cross-sectional area of the cylinder 8 that, with the minimum liquid pressure in the accumulator 3) maintained via the valve 29 at a value approximately equal to the pressure maintained in the delivery passage y14, the increases in the pressure in the accumulator 30 caused as the piston 2 moves towards and into its righthand position ⁇ are never such as to raise the pressure in the cylinder S to a value such that the force exerted by such pressure :on the piston 2 over the limited cross-sectional area of the chamber 8 will exceed the .force applied to the face of the land 3 (whi-ch constitutes the working face of the main working chamber 7) by the delivery pressure in the passage 14.
  • the mean force with which the piston 2 is moved to the left is dependent upon the mean pressure maintained in the accumulator 30 and the relative dimensions of this accumulator and the cylinder and piston .assembly 8, 9 and the stroke of the piston 2, and can be varied by varying the mass of air in the chamber 32 of the accumulator and/or the pressure maintained in the delivery passage 14.
  • the non-return valve 29 is desirable for the non-return valve 29 to be provided with a slight by-pass leak so that, while during normal operation it prevents ow of any appreciable quantity of -liquid past it into the passage 14 as the piston 2 moves to the right, it ⁇ will tend to provide for relatively slow changes in the mean pressure in the accumulator Sil with changes in the pressure maintained in the passage 14.
  • the delivery pressure in the passage ,14 may be varied to vary the force ywith which 4the piston 2 is moved to the left without disturbing the operation of the apparatus because any maintained change in pressure in the passage 14 automatically causes a corresponding change in the mean pressure in the accumulator 30 .as well as changing the pressure available for delivery to the working chamber 7.
  • Hydraulically operated reciprocating apparatus comprising a main working piston .and cylinder assembly including a main working cylinder and a main working piston having a part of larger diameter disposed for reciprocation within the main working cylinder and cooperating therewith to 'form a first working chamber of larger cross-sectional area, a subsidiary working piston and cylinder assembly comprising a subsidiary Working piston .and a subsidiary working cylinder arranged for reciprocation relatively to one another, one of such relatively moving parts 'being rigid with the main Work-ing piston while the other is rigid with the main working cylinder, the subsidiary working cylinder opening into the end of the main working cylinder remote from the said working chamber of larger cross-sectional area and being of smaller cross-sectional area than said working chamber of larger cross-sectional area, lluid pressure supply means, passage means connecting said fluid pressure supply means continuously to said working chamber of smaller cross-sectional area, a hydraulic accumulator having its liquid pressure chamber connected to said passage means, a non-return valve between said liquid pressure chamber tand the part of said passage means
  • said uid pressure supply means comprises ⁇ a pump having a delivery passage communicating with said valve means and through s-aid nonreturn valve, .with said liquid pressure chamber of said accumulator device.
  • Hydraulically operated reciprocating apparatus as claimed in claim 2 including a second yhydraulic accumulator connected to and in continuous open communication with the delivery passage of said pump.
  • Hydraulically operated reciprocating apparatus as claimed in claim 1 including an automatic relief valve permitting escape of iiuid from the end of said main working cylinder remote from said Working chamber of larger cross-sectional area.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid-Pressure Circuits (AREA)
US322652A 1962-12-03 1963-11-12 Hydraulically-operated reciprocating apparatus Expired - Lifetime US3186169A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB4566562 1962-12-03

Publications (1)

Publication Number Publication Date
US3186169A true US3186169A (en) 1965-06-01

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Family Applications (1)

Application Number Title Priority Date Filing Date
US322652A Expired - Lifetime US3186169A (en) 1962-12-03 1963-11-12 Hydraulically-operated reciprocating apparatus

Country Status (2)

Country Link
US (1) US3186169A (de)
DE (1) DE1503334A1 (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3333456A (en) * 1964-12-28 1967-08-01 Prescon Corp Machine for cold heading wire
US3404603A (en) * 1965-04-23 1968-10-08 Vickers Ltd Hydraulically operated tools
US3415159A (en) * 1964-11-14 1968-12-10 Reinhard Hornlein K G Fluid-operated extendable and contractable arrangement
US3869860A (en) * 1972-12-29 1975-03-11 Keelavite Hydraulics Ltd Fluid flow control valves
US4238290A (en) * 1974-06-26 1980-12-09 Kraftwerk Union Aktiengesellschaft Nuclear reactor installation
US4735051A (en) * 1984-06-07 1988-04-05 Veb Kombinat Orsta-Hydraulik Double admitting pressure intensifier
US4895492A (en) * 1982-09-27 1990-01-23 Veb Kombinat Orsta-Hydraulik Double acting and automatically reversing pressure intensifier
US5522221A (en) * 1991-08-07 1996-06-04 Microhydraulics Inc. Active suspension system
WO1996025273A1 (en) * 1995-02-13 1996-08-22 Cams Maskinteknik Ab Method and pressure fluid system for variable exertion of power

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2048550A (en) * 1935-03-29 1936-07-21 Helenberg John Pressure actuated trip valve
US2731796A (en) * 1956-01-24 Hydraulic driving apparatus

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2731796A (en) * 1956-01-24 Hydraulic driving apparatus
US2048550A (en) * 1935-03-29 1936-07-21 Helenberg John Pressure actuated trip valve

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3415159A (en) * 1964-11-14 1968-12-10 Reinhard Hornlein K G Fluid-operated extendable and contractable arrangement
US3333456A (en) * 1964-12-28 1967-08-01 Prescon Corp Machine for cold heading wire
US3404603A (en) * 1965-04-23 1968-10-08 Vickers Ltd Hydraulically operated tools
US3869860A (en) * 1972-12-29 1975-03-11 Keelavite Hydraulics Ltd Fluid flow control valves
US4238290A (en) * 1974-06-26 1980-12-09 Kraftwerk Union Aktiengesellschaft Nuclear reactor installation
US4895492A (en) * 1982-09-27 1990-01-23 Veb Kombinat Orsta-Hydraulik Double acting and automatically reversing pressure intensifier
US4735051A (en) * 1984-06-07 1988-04-05 Veb Kombinat Orsta-Hydraulik Double admitting pressure intensifier
US5522221A (en) * 1991-08-07 1996-06-04 Microhydraulics Inc. Active suspension system
WO1996025273A1 (en) * 1995-02-13 1996-08-22 Cams Maskinteknik Ab Method and pressure fluid system for variable exertion of power

Also Published As

Publication number Publication date
DE1503334A1 (de) 1969-11-06

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Date Code Title Description
AS Assignment

Owner name: COMMERCIAL SHEARING INC.; 1775 LOGAN AVE., YOUNGST

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:SMEC SYSTEMS LIMITED;REEL/FRAME:004103/0882

Effective date: 19821214