US3593519A - Device for precision reversing in a manner substantially independent of load, for use in a hydraulic power drive for reciprocating movements, for instance for machine tools and elevators - Google Patents

Device for precision reversing in a manner substantially independent of load, for use in a hydraulic power drive for reciprocating movements, for instance for machine tools and elevators Download PDF

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Publication number
US3593519A
US3593519A US832066A US3593519DA US3593519A US 3593519 A US3593519 A US 3593519A US 832066 A US832066 A US 832066A US 3593519D A US3593519D A US 3593519DA US 3593519 A US3593519 A US 3593519A
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United States
Prior art keywords
system defined
reversing
feeler
point
valve
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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
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US832066A
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English (en)
Inventor
Paul Fuhrimann
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Schaeffler Schweiz GmbH
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Hydrel AG
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
    • B23Q5/00—Driving or feeding mechanisms; Control arrangements therefor
    • B23Q5/02—Driving main working members
    • B23Q5/027—Driving main working members reciprocating members
    • B23Q5/033—Driving main working members reciprocating members driven essentially by fluid pressure
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/46—Automatic regulation in accordance with output requirements
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/46—Automatic regulation in accordance with output requirements
    • F16H61/47—Automatic regulation in accordance with output requirements for achieving a target output speed
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S60/00—Power plants
    • Y10S60/911—Fluid motor system incorporating electrical system

Definitions

  • Ross ABSTRACT A system for the precision reversal of the motion Of a movable member, such as an elevator, connected to a hydraulic motor.
  • the movable member is provided with a pair of reversing surfaces so shaped as to determine braking distance, reversing point and reacceleration characteristics and cooperating with a feeler which transmits a signal through an amplifier to a servo valve for switching a pump.
  • PAIENIEO JULZO m1 SHEET 1 OF 3 PAUL FU HR I MANN INVENTOR.
  • This invention relates to a device for precision reversing in a manner substantially independent of load, for use in an hydraulic power drive for reciprocating movements, for instance for machine tools and elevators, having a main oil pump delivering through the idle point in both drive directions alternately for the drive of a rotary hydraulic motor or a doubleacting piston-and-cylinder motor with rapid reversing of the movement and ascertainment of an accurate reversing point of the movable element of the motor depending on the running distance covered by said movable element and on the shape and location of adjustable control elements, and further having a servo oil circuit with servo pump allocated to the main oil pump and a voltage-dependent electrohydraulic serv
  • the present invention solves the problem by far simpler means by providing reversing surfaces on the reciprocating machine or elevator part or on a-tup connected to and moving with it for the purpose of establishing the reversing characteristic including the braking distance, reversing point and reacceleration distance, and by placing-the middle of the path of these reversing surfaces a feeler of an electric control member that is actuating by said surfaces.
  • the control member is connected via an electronic amplifier to an'solenoid of the electrohydraulic servo valve for the purpose of transmitting electric values of the member corresponding to the momentary position of the reversing surfaces relative to the feeler.
  • the arrangement is such that every point of contact between the feeler and the reversing surface corresponds'in the control member to a definite capacitive, inductive or voltage value, which values are transmitted via the-electronic amplifier to the .eleetrohydraulic servo valve which in turn controls the oil-driving pump, equipped for regulation through the idle point, in respect to the required delivery .quantities, within the range of the freely adjustable maximum speeds of the motor both for forward and reverse motion.
  • FIG. I is a diagram of the installation
  • FIG. 2 is a diagrammatic representation of the variationsaof voltage in the servo valve during the reversing phase
  • FIG. 3 is a graphic representation of the pump delivery during the reversing phase
  • FIG. 4 is a displacement velocity diagram in the reversing range of the reciprocating machine or elevator part or of the tu
  • numeral 1 designates a-main oil pump delivering in both directions of rotation and reversing through its idle or null point. It communicates through pipes 2 and 3 with an hydraulic motor 4.
  • Main oil pump 1, pipes 2 and 3 and hydraulic motor 4 form a closed circuit.
  • Main oil pump 1 is equipped with a voltage-controlled servovalve 5 which, on the one hand communicates through a pipe 6 with an auxiliary or control oil pump 7 and, on the other hand, is connected through an electric lead 8 to the electronic amplifier 9 of an electronic set 10 which is equipped with a pair of velocity regulators 9, one each for the working velocity VA and the return velocity VR. With these regulators, the two velocities that may be required in any given case can be set in the form of maximum values.
  • Numeral ll designatesa feed and flushing block 11 of known design connected in parallel with the main oil pump 1, which communicates through pipes 12 and 13 with pipes-2 and 3 leading to hydraulic motor 4.
  • An overflow pipe 14 leads from the feed and flushing block II to the oil tank 15.
  • the bypass valve 16 is connected in parallel with the main oil pump 1 and is connected by pipes 17 and 18 to pipes 2 and 3 leading to hydraulic motor'4.
  • the hydraulic motor is connected by gears 19 and 20 to a screw spindle 21 adapted to serve as a drive for a tup 22 or for the reciprocating part of the machine or elevator.
  • Control elements 23 and 24 are arranged on the tup or the machine or elevator part (driven member) 22 so that theycan be displaced and fixed in the desired position.
  • Each of the control elements has a specially designed control surface 23 and 24 respectively, into the path of which the end 25'of a linearly movable feeler 25 projects.
  • Fecler 25 is in interacting connection with a linear potentiometer 26 of the transducer means which is connected through an electric lead 27 to the electronic block 10 including, in addition to the amplifier set 9, a voltage seesaw device 28.
  • a second pipe 30'with a pressure relief or nonretum valve 31 is also connected to control oil pump 7, or more exactly to pipe 6, and leads into the oil tank 15.
  • the main oil pump 1 delivers pressurized oil through pipe 2 to hydraulic motor 4, and let us further assume that the tup 22 is thereby moved through gear 19 and 20' and screw spindle 21 in the direction ofarrow A (FIG. I) at a maximum constant speed set by the velocity regulator 9 shown in FIG. 1.
  • tup 22 has covered the free path between reversing elements 23' and 24, reversing surface 24 runs up against the end 25 of feeler 25, so that the feeler is displaced in the direction of arrow B.
  • a change in voltage is brought about in linear potentiometer 26.
  • This voltage change acts through the-electric lead 27, the amplifier set 9 and a solenoid of servo valve 5 to regulate the pressure of the oil supplied by auxiliary pump 7to the servo valve .for the adjustment of the eccentricity (displacement) of themain oil pump 1, which can be regulated both with respect to its delivery quantity and to the direction of delivery.
  • the comparatively small change in electric voltage of the linear potentiometer is converted by amplifier set 9 and servo 'valve 5 into a correspondingly large mechanical force which moves the main oil pump into the desired swivel position so that the delivery of the pump falls almost to zero, whereupon the pump, reaching the tripping point, springsin the opposite direction and now forces pressurized oil through pipe 3 to hydraulic motor 4.
  • the feed and flushing block 11 ensures the replacement of the leakage loss of oil due to the pressure in the closed oil-circuit l, 2, 3 and 4 and an exchange of oil, and therewith the venting of oil pipes 2 and 3 which are alternately under pressure and not, so as to prevent overheating of the oil although it is exposed to constant pressure impacts and is-in reciprocating additional braking of the hydraulicmotor 4, the bypass valve 16 has as its 'purpose to ensure the balancing of 'any small quantity of oil that may still be flowing when the main pump 1 is out of operation, but because of certain inaccuracies a very small amount of oil should be supplied to the hydraulic motor.
  • the voltage seesaw device 28 serves both to skip the zero-voltage point zero-velocity point of the last braking and first reacceleration phase and thus also to prevent the effective zero voltage from being reached, while at the same time supplying the necessary initial voltage for reacceleration.
  • FIG. 2 the variations of voltage in the servo valve are shown graphically.
  • Line (branch) K shows the drop in voltage as the tup runs up against the reversing surface.
  • the voltage seesaw device comes into action, at a voltage value in the servo valve of at least about 1 percent of the maximum voltage. denotes the point of zero voltage, while P is the rise of the voltage after reversing has taken place.
  • FIG. 3' the pump delivery corresponding to the voltage variation of FIG. 2 is represented graphically, line (branch) V being the drop in delivery as a result of the slowing of the speed as caused by the reversing surface, while line (branch) B shows the increase in the pump delivery in the acceleration phase.
  • the reversing path during the tripping over of the volt age is designated s.
  • FIG. 4 the velocity curve is shown graphically in a solid line for uniform braking and acceleration, the straight lines E and E holding good for constant velocities of the tup when the, reversing elements 23 and 24 are outside the range of feeler 25,25.
  • the oblique straight line F shows the velocity controlled by potentiometer 26 and falling almost to the zero line N during the braking process, while the oblique straight line G represents the corresponding reacceleration phase. Sk marks the bridging phase when the voltage trips over.
  • the velocity E till the commencement of braking is 90 meters per minute, for instance, it will be only 60 meters per minute at point a, 30 meters per minute at point b and 6 meters per minute at point c.
  • acceleration begins in the reverse direction of operation. The velocity at point dis 6 meters per minute, at e 30, atf 60 and at E reaches the normal level of 90 meters per minute.
  • FIG. 4 further shows, with linear control of the curve by the potentiometer the braking and reacceleration phases run out in a fairly long peak. This peak can be considerably shortened by using a parabolic or sinusoidal curve.
  • the course taken by braking and reacceleration in this case is shown in FIG. 4 by the curves H and .l.
  • a similar effect is obtained if the profile of the reversing surfaces is shaped in accordance with an exponential curve with an exponent greater than unity.
  • An axial-pison-type pump can be used advantageously for the main oil pump 1, while a piston-and-cylinder system may be used instead of the hydraulic motor 4.
  • the reversing surfaces 23 and 24 their profile may be shaped in various ways, for instance as an oblique straight line or, as already mentioned, as an exponential curve. It might also be conceivable to have the profiles of the reversing surfaces designed in sinusoidal or parabolic form or to combine some of these different profiles.
  • a hydraulic motor connected to said load for reciprocating same; a main oil pump connected in a fluid circuit 'with said hydraulic motor and having two fluid drive directions separated by an idle point for powering said hydraulic motor in opposite directions; a servo Oll circuit including a servo pump, anelectrically operated servocontrol valve connected to said servo pump and to said main oil pump for reversibly switching same between said directions through said idle point, and transducer means fortransforming a mechanical movement into an electrical signal applied to said valve; and
  • transducer means including an electric control feeler actuated by said surfaces and disposed between them, said surfaces and feeler being so constructed and arranged that each point of contact of said feeler with said surfaces corresponds to an electrical parameter transmitted to said valve for controlling said main oil pump through said idle point to deliver corresponding quantities of a fluid medium to corresponding sides of said motor.
  • said electric control feeler includes a capacitively regulatable condenser.
  • each of said surfaces lies along a respective composite curve consisting of a plurality of shapes including a straight line, a sinusoid, a parabola and an exponential curve.
  • control element mounted on said member and carrying said surfaces, said control element being movable relatively to said member and said feeler and being adapted to be secured to said member in a selected one of a number of positions.
  • transducer means includes a voltage seesaw device adapted to skip the electrical signal value corresponding to the zero-velocity point of said member and to switch over directly to an electrical parameter producing reacceleration.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Types And Forms Of Lifts (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Control Of Fluid Gearings (AREA)
US832066A 1968-09-10 1969-06-11 Device for precision reversing in a manner substantially independent of load, for use in a hydraulic power drive for reciprocating movements, for instance for machine tools and elevators Expired - Lifetime US3593519A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH1369068A CH477630A (de) 1968-09-10 1968-09-10 Mindestens angenähert lastunabhängige Genauigkeitsumsteuerung an einem hydraulischen Leistungsantrieb für Wechselbewegungen eines Arbeitsorganes, beispielsweise bei Werkzeugmaschinen und Aufzügen

Publications (1)

Publication Number Publication Date
US3593519A true US3593519A (en) 1971-07-20

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US832066A Expired - Lifetime US3593519A (en) 1968-09-10 1969-06-11 Device for precision reversing in a manner substantially independent of load, for use in a hydraulic power drive for reciprocating movements, for instance for machine tools and elevators

Country Status (8)

Country Link
US (1) US3593519A (xx)
JP (1) JPS4945669B1 (xx)
AT (1) AT293820B (xx)
CH (1) CH477630A (xx)
DE (1) DE6918885U (xx)
FR (1) FR2017998A1 (xx)
GB (1) GB1229537A (xx)
SE (1) SE370892B (xx)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5048294A (en) * 1987-11-28 1991-09-17 Hitachi Construction Machinery Co., Ltd. Safety device for hydraulic closed circuit
US5072584A (en) * 1987-03-27 1991-12-17 Magnus Mauch Hydraulic drive with fluid cooling by-pass line
US6145312A (en) * 1998-12-30 2000-11-14 Hydro-Gear Limited Partnership Electro-mechanical bypass for hydrostatic transmission
US6430923B1 (en) * 2000-08-18 2002-08-13 Sauer-Danfoss Inc. Loop flushing circuit
US6672843B1 (en) * 2002-04-08 2004-01-06 Hydro-Gear Limited Partnership Dual pump apparatus comprising dual drive shafts and auxiliary pump
US6735943B1 (en) 1998-12-30 2004-05-18 Hydro-Gear Limited Partnership Bypass for a hydraulic device
US20040187491A1 (en) * 2003-03-26 2004-09-30 Whitaker James S. Pump with hot oil shuttle valve
US7007467B1 (en) * 1998-12-30 2006-03-07 Hydro-Gear Limited Partnership Bypass for a hydraulic device
US7229256B1 (en) 2003-03-11 2007-06-12 Hydro-Gear Limited Partnership Dual pump transmission
US7275371B1 (en) 1998-12-30 2007-10-02 Hydro-Gear Limited Patnership Bypass for a hydraulic device
US20100095665A1 (en) * 2008-10-21 2010-04-22 Caterpillar Inc. Hydrostatic pump and motor with improved torque reversal characteristics

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5133061U (xx) * 1974-08-30 1976-03-11

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1948951A (en) * 1929-08-21 1934-02-27 Walker Brooks Hydraulic power unit
US2299686A (en) * 1940-01-15 1942-10-20 Hydraulic Dev Corp Inc Hydraulic press
US2324727A (en) * 1941-01-10 1943-07-20 Vickers Inc Power transmission
US2388369A (en) * 1944-10-30 1945-11-06 Shendrick Constantine Fluid control valve
US2419563A (en) * 1942-12-11 1947-04-29 Hydraulic Dev Corp Inc Hydraulic press for stepwise drawing of metal

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1948951A (en) * 1929-08-21 1934-02-27 Walker Brooks Hydraulic power unit
US2299686A (en) * 1940-01-15 1942-10-20 Hydraulic Dev Corp Inc Hydraulic press
US2324727A (en) * 1941-01-10 1943-07-20 Vickers Inc Power transmission
US2419563A (en) * 1942-12-11 1947-04-29 Hydraulic Dev Corp Inc Hydraulic press for stepwise drawing of metal
US2388369A (en) * 1944-10-30 1945-11-06 Shendrick Constantine Fluid control valve

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5072584A (en) * 1987-03-27 1991-12-17 Magnus Mauch Hydraulic drive with fluid cooling by-pass line
US5048294A (en) * 1987-11-28 1991-09-17 Hitachi Construction Machinery Co., Ltd. Safety device for hydraulic closed circuit
US7007467B1 (en) * 1998-12-30 2006-03-07 Hydro-Gear Limited Partnership Bypass for a hydraulic device
US6145312A (en) * 1998-12-30 2000-11-14 Hydro-Gear Limited Partnership Electro-mechanical bypass for hydrostatic transmission
US6332317B1 (en) 1998-12-30 2001-12-25 Hydro-Gear Limited Partnership Bypass for hydrostatic transmission
US6588206B1 (en) 1998-12-30 2003-07-08 Hydro-Gear Limited Partnership Method for controlling fluid flow in a hydrostatic transmission
US6735943B1 (en) 1998-12-30 2004-05-18 Hydro-Gear Limited Partnership Bypass for a hydraulic device
US7275371B1 (en) 1998-12-30 2007-10-02 Hydro-Gear Limited Patnership Bypass for a hydraulic device
US6430923B1 (en) * 2000-08-18 2002-08-13 Sauer-Danfoss Inc. Loop flushing circuit
US7320577B1 (en) 2002-04-08 2008-01-22 Hydro-Gear Limited Partnership Dual pump transmission
US6672843B1 (en) * 2002-04-08 2004-01-06 Hydro-Gear Limited Partnership Dual pump apparatus comprising dual drive shafts and auxiliary pump
US7566207B1 (en) 2002-04-08 2009-07-28 Hydro-Gear Limited Partnership Dual pump transmission
US7229256B1 (en) 2003-03-11 2007-06-12 Hydro-Gear Limited Partnership Dual pump transmission
US7806667B1 (en) 2003-03-11 2010-10-05 Hydro-Gear Limited Partnership Dual pump
US8272315B1 (en) 2003-03-11 2012-09-25 Hydro-Gear Limited Partnership Dual pump
US20040187491A1 (en) * 2003-03-26 2004-09-30 Whitaker James S. Pump with hot oil shuttle valve
US20100095665A1 (en) * 2008-10-21 2010-04-22 Caterpillar Inc. Hydrostatic pump and motor with improved torque reversal characteristics
US8205444B2 (en) 2008-10-21 2012-06-26 Caterpillar Inc. Hydrostatic pump and motor with improved torque reversal characteristics

Also Published As

Publication number Publication date
JPS4945669B1 (xx) 1974-12-05
DE6918885U (de) 1974-01-17
AT293820B (de) 1971-10-25
GB1229537A (xx) 1971-04-21
DE1923740A1 (de) 1970-03-19
SE370892B (xx) 1974-11-04
CH477630A (de) 1969-08-31
DE1923740B2 (de) 1972-09-21
FR2017998A1 (xx) 1970-05-29

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