US3707881A - Control system for hydraulic fluid-feed mechanism - Google Patents

Control system for hydraulic fluid-feed mechanism Download PDF

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Publication number
US3707881A
US3707881A US00121713A US3707881DA US3707881A US 3707881 A US3707881 A US 3707881A US 00121713 A US00121713 A US 00121713A US 3707881D A US3707881D A US 3707881DA US 3707881 A US3707881 A US 3707881A
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US
United States
Prior art keywords
valve
limit control
piston
control
limit
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
US00121713A
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English (en)
Inventor
H Neuhaus
H Peters
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.)
ThyssenKrupp Industrial Solutions AG
Original Assignee
Uhde GmbH
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.)
Filing date
Publication date
Priority claimed from DE19702011570 external-priority patent/DE2011570C/de
Application filed by Uhde GmbH filed Critical Uhde GmbH
Application granted granted Critical
Publication of US3707881A publication Critical patent/US3707881A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
    • F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
    • F16K11/0716—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides with fluid passages through the valve member
    • 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
    • F01L15/00—Valve-gear or valve arrangements, e.g. with reciprocatory slide valves, other than provided for in groups F01L17/00 - F01L29/00
    • F01L15/08—Valve-gear or valve arrangements, e.g. with reciprocatory slide valves, other than provided for in groups F01L17/00 - F01L29/00 with cylindrical, sleeve, or part-annularly-shaped valves; Such main valves combined with auxiliary valves
    • 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
    • F01L25/063—Arrangements with main and auxiliary valves, at least one of them being fluid-driven the auxiliary valve being actuated by the working motor-piston or piston-rod
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
    • F04B9/113—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting liquid motor

Definitions

  • a T TOR NEYS PATENTEDJM 2 1915 saw 3 or 4 INVENTOR.
  • HEI NZ NEUHAUS BY Wadi DR. HENNING PETERS ATTORNEYS CONTROL SYSTEM FOR HYDRAULIC FLUID- FEED MECHANISM BACKGROUND OF THE INVENTION
  • the present invention relates to a control system for hydraulic fluid-feed mechanisms intended to produce straight-line reciprocating motions that are typical preferably for piston pumps and plunger pumps and machine tools.
  • the hydraulic fluid usually oil
  • the working piston moves towards the pressureless cylinder end and, by means of a rigid linkage, its motion is transferred to the working machine, for example to the plungers or pistons of pumps or to the carriages of machine tools.
  • Limit control valves or limit switches are intended to effect the change-over of the multiway valve. While fluid delivered by the hydraulic pump is admitted through the multiway valve into the cylinder to one side of the piston, the fluid on the other side of the piston leaves the cylinder at low pressure through the multiway valve into the return or reflux line.
  • the control system for hydraulic fluid-feed mechanisms therefore, consists essentially of the two limit control valves or limit switches, the multiway valve and, possible, impulse amplifiers.
  • Limit control elements may operate upon the multiway valve either mechanically or through hydraulic, pneumatic or electric transmission.
  • the multiway valve must be located in the vicinity of said elements because they operate directly on the multiway valve.
  • the disadvantage of these mechanical limit control elements is that they do not open quickly the entire necessary cross-sectional area in the multiway valve for the hydraulic fluid; instead, the rate of opening is proportional to the speed of the reciprocating machine element.
  • the multiway valve may be located at a distance from said elements.
  • the conventional hydraulically or pneumatically operating limit control valves have, however, the disadvantage that the control piston is actuated through its entire stroke by the reciprocating machine element; this means that the control piston moves at a speed that corresponds to the speed of the reciprocating machine element. This speed, however, is insufficient for the reversing action.
  • the reversing action can be shortened by using a pneumatic limit control valve with a very short travel followed by a series of pneumatic amplifiers of progressively upward rating depending on the rating of the hydraulic multiway valve. Obviously, this system is necessarily very expensive.
  • a quick reversing action can also be achieved by using an electrically operating control system consisting of limit control element and multiway valve.
  • electric control devices also have inherent disadvantages, such as wear of contactors, faulty contacts, difficulties in locating faults in the electric system and an expensive design for use in areas or plants where explosion hazards are encountered.
  • the action of force of the return spring is opposed to the direction of motion of the control piston when the interlocking pressure becomes effective.
  • the working piston of two or more mechanisms can be connected in parallel in that the limit control valves of one side, i.e., of the same direction of motion, of several mechanisms are interconnected through the interlocking lines of these limit control valves.
  • the limit control valves for the opposite direction of motion are not interconnected.
  • the invention incorporates the particular advantage that, referring to the limit control valve, a minute initiating stroke measuring a fraction of a millimeter is sufficient to achieve a rapid control stroke of several millimeters and, consequently, to cause a quick breakdown of the pressure on one side of the working piston and a quick build-up of pressure on the opposite side of the piston.
  • this method makes it possible to obtain an almost ideal rectangular discharge diagram.
  • the pressure on the working piston remains effective until the piston has reached its end position, then breaks down suddenly while becoming fully effective on the opposite side.
  • the use of the subject control system results in very short dead periods and, consequently, reduced machining time.
  • control cam on the working piston rod will contact the head of the control piston for a short time only and move it a fraction of a millimeter into the valve.
  • the return spring then acts to draw the head of the control piston away from the control cam.
  • the limit control valve cannot be damaged by the control cam or the working piston rod.
  • FIG. 1 is a schematic diagram of a hydraulic cylinder control system constructed according to the invention with the parts shown in neutral positions.
  • FIG. 2 is a cross section of a limit control valve or pilot valve used in the control system of FIG. 1, with the valve stem in extended position.
  • FIG. 3 is similar to FIG. 2 with the valve stem in retracted position.
  • FIG. 4 is a schematic diagram similar to FIG. 1 showing the valve positions as a transfer or reversal of the power cylinder is being completed.
  • FIG. 5 is a schematic diagram of two control systems connected for synchronous operation.
  • the hydraulic fluid-feed mechanism consists essentially of the system comprising the mechanism and the control and interlocking facilities.
  • the fluid is admitted through multiway valve 1 alternately to the two sides of working piston 2 by means of a pump that has been omitted from the drawing for better clarity.
  • the fluid returns from the depressurized cylinder end through the multiway valve 1 to a pump suction tank.
  • the pump for the control system S the pump has also been omitted from the drawing --produces the constant control pressure ahead of limit control or pilot valves 3 and 3'.
  • the interlocking system V consists of the limit control valves with the control lines between limit control valves 3 and 3 and multiway valve 1. Return lines R on the limit control valves are provided to achieve an alternate pressure release on piston 4 in the multiway valve.
  • Each of the two limit control valves consists essentially of a valve body 5, two covers 6 and 7, control sleeve 8, control piston 9 and return spring 10.
  • Valve body 5 is provided with a pressure control-fluid connection B, a return connection C and a connection D for an interconnecting line between the limit control valve 3 and the multiway valve 1.
  • Each cover 6 is provided with a connection E for one of the interlocking lines V. Referring to known control systems, this connection serves for leak oil discharge-
  • the limit control valve has two stable positions: a working position and a zero position. In the working position, as shown in FIG. 2, the control piston 9 extends from the valve in position to be actuated by the moving machine, for example a plunger pump.
  • connection E the control piston is forced into the extended or working position by the pressure in one line of the interlocking system and against the force of the return spring, the pressure being admitted through connection E.
  • the return spring is being compressed.
  • Connections D and C are communicating with return line R through piston recess 11 and are, therefore, pressureless.
  • Control line 12 connected at D and leading to the multiway valve is also pressureless.
  • the control pressure admitted to connection B remains ineffective because the flow from B through piston recess 13 is obstructed.
  • a cam 14 on the working piston rod contacts piston head roller 15 of the control piston, the latter will start moving into the valve and establish communication between connection B and connection D through piston recess 13 as may be noted from FIG. 3.
  • the control system for a multicylinder mechanism may comprise a plurality of systems as shown in FIG. 5 interconnected to operate in synchronism.
  • a first system similar to that shown in FIGS. 1 and 4 is shown in the upper part of the figure and the parts identified with corresponding numerals with a suffix a.
  • a second similar system is shown in the lower part of the figure and the parts identified with corresponding numerals with a suffix b.
  • the two systems and any others to be operated in synchronism therewith are connected by leads b and c.
  • the pump for the fluid-feed is adequately sized to permit simultaneous operation of both working pistons.
  • the several fluid-feed mechanisms A are connected to the pump discharge line at a.
  • One multiway valve la, lb and two limit control valves 3a, 3'a; 3b, 3'b with control system and interlocking system are associated with each working piston.
  • the two control systems are fed from one pump and are interconnected through connection b. Synchronous operation of the two working pistons is achieved by interconnecting the two control lines 12a, 12b through connection c.
  • the interlocking lines 18a, 18b are also connected to each other.
  • the two limit control valves 3'0, 3b for the opposite direction of travel are not interconnected or interlocked since the pressure changes in the lines 12a, 12b; 18a, 18b as a result of operating one pair of limit control valves can hydraulically operate the other interconnected pairs of valves.
  • shutoff valves or change-over valves on the interconnecting lines makes it possible to disconnect individual systems, for example for part-load operation or repair work.
  • a control system for a hydraulically actuated valve of a hydraulic power cylinder assembly comprising, in combination, a pair of limit control valves, a spring in each limit control valve for urging the valve in a first direction, a piston and cylinder in each limit valve for urging the valve in a second direction, means responsive to approach of the power cylinder assembly to an end of its stroke for initiating movement of one of the limit control valves, ports in each limit control valve and fluid conduit means connecting a source of contro fluid through the ports in one limit control valve to the piston and cylinder of the other limit control valve and to an end of the hydraulically actuated valve, said piston and cylinder and said spring cooperating to position the limit control valve in response to control fluid supplied through the other limit control valve following an initial movement of one of the limit control valves.
  • a limit control valve according to claim 1 in which the spring urges the valve toward its inactive position and the fluid pressure admitted through the other valve to the piston and cylinder urges the valve toward its working position.
  • a limit control valve system including fluid conduit means interconnecting first ones of a plurality of pairs of limit control valves in parallel for synchronous operation.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
US00121713A 1970-03-12 1971-03-08 Control system for hydraulic fluid-feed mechanism Expired - Lifetime US3707881A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19702011570 DE2011570C (de) 1970-03-12 Steuersystem für druckmittelbetriebene Antriebe

Publications (1)

Publication Number Publication Date
US3707881A true US3707881A (en) 1973-01-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00121713A Expired - Lifetime US3707881A (en) 1970-03-12 1971-03-08 Control system for hydraulic fluid-feed mechanism

Country Status (7)

Country Link
US (1) US3707881A (nl)
JP (1) JPS5514274B1 (nl)
CH (1) CH526051A (nl)
FR (1) FR2081893B1 (nl)
GB (1) GB1349083A (nl)
NL (1) NL168589C (nl)
SE (1) SE367461B (nl)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4002103A (en) * 1974-07-01 1977-01-11 The West Company Reciprocating apparatus with a controllable dwell time at each end of the stroke
US4242940A (en) * 1977-05-30 1981-01-06 Page Victor J Fluid operated control device
US4368008A (en) * 1981-02-10 1983-01-11 Tadeusz Budzich Reciprocating controls of a gas compressor using free floating hydraulically driven piston
WO2000077397A1 (fr) * 1999-06-15 2000-12-21 Bernard Marinzet Pompe a pistons, procede et installation de filtration d'eau
WO2005121555A1 (en) * 2004-06-07 2005-12-22 Hunter Hitech Pty Ltd A pump assembly
CN102094780A (zh) * 2011-01-21 2011-06-15 晋中开发区宏光实业有限公司 液压泥浆泵
AU2005252262B2 (en) * 2004-06-07 2011-07-28 Hitech Hippo Australia Ltd A pump assembly
CN102937074A (zh) * 2012-11-12 2013-02-20 三一重工股份有限公司 连续供料系统及其控制方法、登高平台消防车
US20140199182A1 (en) * 2013-01-11 2014-07-17 Super Products Llc Reciprocating water pump
US9233340B1 (en) * 2015-01-13 2016-01-12 Renergy Technologies Ltd. Cylinder arrangement and method of use for energy recovery with seawater desalination
CN106870316A (zh) * 2017-04-18 2017-06-20 黄山市汇润机械有限公司 一种液压式双作用压力泵橇
US20170184090A1 (en) * 2013-01-11 2017-06-29 Super Products Llc Reciprocating water pump

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE430532B (sv) * 1981-01-16 1983-11-21 Blidsberg Verktygsind System for tillforsel av ett kompressibelt drivmedium
US4522033A (en) * 1984-07-02 1985-06-11 Cvi Incorporated Cryogenic refrigerator with gas spring loaded valve

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1577914A (en) * 1921-11-08 1926-03-23 Cain John A Le Steam-engine valve gear
US2296647A (en) * 1941-02-28 1942-09-22 Racine Tool & Machine Company Hydraulic pressure booster
US2698517A (en) * 1952-05-21 1955-01-04 Kenneth F Witt Automatic means to control and reverse fluid-operated cylinder-and-piston units
US3225663A (en) * 1963-04-09 1965-12-28 Hispano Suiza Sa Hydraulic control systems including double action receiver apparatus

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH473319A (de) * 1968-06-19 1969-05-31 Hydrel Ag Maschf Vollhydraulische Vorrichtung an Maschine oder Apparat mit geradlinig hin- und hergehendem Teil, für weitgehend last- und geschwindigkeitsunabhängige Genauigkeitsumsteuerung der Bewegung des Teils zwischen zwei einstellbaren Umsteuerpunkten

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1577914A (en) * 1921-11-08 1926-03-23 Cain John A Le Steam-engine valve gear
US2296647A (en) * 1941-02-28 1942-09-22 Racine Tool & Machine Company Hydraulic pressure booster
US2698517A (en) * 1952-05-21 1955-01-04 Kenneth F Witt Automatic means to control and reverse fluid-operated cylinder-and-piston units
US3225663A (en) * 1963-04-09 1965-12-28 Hispano Suiza Sa Hydraulic control systems including double action receiver apparatus

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4002103A (en) * 1974-07-01 1977-01-11 The West Company Reciprocating apparatus with a controllable dwell time at each end of the stroke
US4242940A (en) * 1977-05-30 1981-01-06 Page Victor J Fluid operated control device
US4368008A (en) * 1981-02-10 1983-01-11 Tadeusz Budzich Reciprocating controls of a gas compressor using free floating hydraulically driven piston
WO2000077397A1 (fr) * 1999-06-15 2000-12-21 Bernard Marinzet Pompe a pistons, procede et installation de filtration d'eau
US6652741B1 (en) 1999-06-15 2003-11-25 Bernard Marinzet Piston pump, method and installation for filtering water
AU2005252262B2 (en) * 2004-06-07 2011-07-28 Hitech Hippo Australia Ltd A pump assembly
US20110044830A1 (en) * 2004-06-07 2011-02-24 Hunter Hitech Pty Ltd Pump assembly
WO2005121555A1 (en) * 2004-06-07 2005-12-22 Hunter Hitech Pty Ltd A pump assembly
CN102094780A (zh) * 2011-01-21 2011-06-15 晋中开发区宏光实业有限公司 液压泥浆泵
CN102937074A (zh) * 2012-11-12 2013-02-20 三一重工股份有限公司 连续供料系统及其控制方法、登高平台消防车
CN102937074B (zh) * 2012-11-12 2015-06-10 三一汽车制造有限公司 连续供料系统及其控制方法、登高平台消防车
US20140199182A1 (en) * 2013-01-11 2014-07-17 Super Products Llc Reciprocating water pump
US20170184090A1 (en) * 2013-01-11 2017-06-29 Super Products Llc Reciprocating water pump
US9233340B1 (en) * 2015-01-13 2016-01-12 Renergy Technologies Ltd. Cylinder arrangement and method of use for energy recovery with seawater desalination
CN106870316A (zh) * 2017-04-18 2017-06-20 黄山市汇润机械有限公司 一种液压式双作用压力泵橇
CN106870316B (zh) * 2017-04-18 2019-06-11 黄山市汇润机械有限公司 一种液压式双作用压裂泵橇

Also Published As

Publication number Publication date
NL168589B (nl) 1981-11-16
JPS5514274B1 (nl) 1980-04-15
NL168589C (nl) 1982-04-16
GB1349083A (en) 1974-03-27
FR2081893A1 (nl) 1971-12-10
CH526051A (de) 1972-07-31
NL7101639A (nl) 1971-09-14
SE367461B (nl) 1974-05-27
FR2081893B1 (nl) 1974-10-31
DE2011570A1 (de) 1971-09-30

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