US3842855A - Hydrostatic flow-amplifier - Google Patents

Hydrostatic flow-amplifier Download PDF

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Publication number
US3842855A
US3842855A US82847669A US3842855A US 3842855 A US3842855 A US 3842855A US 82847669 A US82847669 A US 82847669A US 3842855 A US3842855 A US 3842855A
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United States
Prior art keywords
disc
seat
pressure area
load
pressure
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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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English (en)
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I Cyphelly
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Moog GAT GmbH
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Individual
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Filing date
Publication date
Priority claimed from CH961668A external-priority patent/CH492886A/de
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Publication of US3842855A publication Critical patent/US3842855A/en
Assigned to GLYCO-ANTRIEBSTECHNIK GMBH reassignment GLYCO-ANTRIEBSTECHNIK GMBH ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CYPHELLY, IVAN J.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • 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
    • Y10T137/2278—Pressure modulating relays or followers
    • 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
    • Y10T137/2278—Pressure modulating relays or followers
    • Y10T137/2409—With counter-balancing pressure feedback to the modulating device

Definitions

  • ABSTRACT D The amplifier has a poppet valve enclosing a high F g Appllcatlon y Data pressure area, an intermediate pressure area con- Oct. 30, 1968 Switzerland 16194/68 nected to a reference pressure by another valve, and a June 27, 1968 Switzerland 9616/68 load pressure area, and with a throttling disc as the poppet.
  • the disc cooperates with a control seat and a [52] US. Cl. 137/85, 137/82 v load seat.
  • FIGS. 1 and 2 are schematic sectional views through a plane hydrostatic flow-amplifier
  • FIG. 4 is a functional diagram of the servo loop
  • FIG. 5 shows the corresponding equivalent system using conventional components
  • FIG. 6 is a schematic view in cross section of another embodiment of the invention.
  • FIG. 6a shows the corresponding equivalent system using conventional components
  • FIG. 7 is a schematic view in cross section of a hydrostatic flow-amplifier with an adjustable control seat
  • FIG. 7a shows the corresponding equivalent system using conventional components
  • FIG. 9 is a schematic view in cross section of a hydrostatic flow-amplifier arranged as the balanced throttle of three sealed load loops.
  • FIG. 9a shows the corresponding equivalent system using conventional components
  • FIG. 10 is a cross sectional view of an embodiment combining the amplifiers shown in FIGS. 6 and 8, and having a viscothermic throttle.
  • FIG. 11 is a vertical sectional view of a screw valve.
  • FIG. 12 is a vertical sectional view of an electromagnetically operated flapper valve.
  • FIG. 1 shows a supply pressure line 1, which opens through a seat member 2 into a high pressure area 3 of the amplifier.
  • a throttling disc 4 acting as the poppet of a poppet valve and which is movable at right angles to the stationary, lower seat member 2, forms throttling gaps 5 and 6, the gap 5 separating the high pressure area 3 from an intermediate pressure area 7 and the gap 6 separating the high pressure area 3 from a load pressure area 8.
  • the throttling disc 4 is enclosed by a housing 9.
  • suitable throttling devices can be screwed into this housing, such as a screw valve 10 or an electromagnetically operated flapper valve 11, as shown in FIGS.
  • FIG. 2 is a cross sectional view through the throttling gaps 5 and 6 and at right angles to the direction of movement of the throttling disc 4.
  • High pressure delivery branches l2, fed from the line 1, and the mouth 13 of a load pressure line are visible in FIG. 2.
  • the branches 12 are also visible in FIG. 1, but are not referenced.
  • Grooves in the stationary seat member 2 form the continuous high pressure area 3 and the load pressure area 8, these two areas being separated by a labyrinthine load seat 14.
  • the entire space is enclosed by the housing 9, which has rail-like projections 15 that guide the throttling disc in its movements.
  • the position of the throttling disc 4 in other words, the width of the control throttling gap is determined by a controllable device, such as the flapper valve 11. Since, in accordance with the invention, the load throttling gap width at 6 changes with the control throttling gap width 5, a change of the flapper valve 11 results in a corresponding change in the load flow, caused by movement of the throttling disc 4.
  • the poppet valve (of which the throttling disc 4 is the poppet) acts like a hydrostatic flowamplifier; and the high pressure area 3, the control throttling gap 5, the theottling disc 4, and the intermediate pressure area 7 form a servo loop, which will be explained with reference to FIGS. 3 and 4.
  • FIG. 3 h denotes the gap width, which, if the underside of the throttling disc 4 is flat, is common to the load seat and the control seat, the latter seat being formed by that part of the seat member 2 defining, with the disc 4, the gap 5.
  • the intermediate pressure p existing above the throttling disc exerts on the latter a force F,
  • the high pressure p and the load pressure p acting on the under surface of the throttling disc produce a force F,, opposing the force F,; if these two forces are equal, the throttling disc is in a stable rest position.
  • the servo loop corresponding to this system is shown in FIG. 4. Since the controlled member G, is in the same way dependent on the setting of the valve (10 or 11) as is the control feedback G the output it is a function of d, which is the desired effect.
  • the equivalent system illustrated in FIG. 5, consists of conventional hydraulic elements that would act in a way similar to that of the flow-amplifier.
  • the control throttling gap 5 is represented by an adjustable throttle 5' and the load throttling gap 6 by an adjustible throttle 6', these two throttles being operated by a differential jack 4 that corresponds to the throttling disc 4.
  • the differential jack is analogously'acted upon by all of the pressures that occur in the amplifier.
  • the supply pressure line in agreement with FIG. 1, is again denoted by the reference numeral 1 and the load pressure line by the numeral 13, in agreement with FIG. 2.
  • the line leading from the load pressure line 13 to the differential jack 4 represents, in accordance with FIG. 3, the load pressure acting directly on the throttling disc.
  • FIGS. 1 and 2 ensures between the control flow and the load fiow a ratio of 100 that is virtually independent of the high pressure and the viscosity. Higher amplifications can be obtained by changing the geometry.
  • FIGS. 6a, 7a, 8a and 9a also contains the equivalent system, which reproduces with conventional components the function of the corresponding amplifier.
  • FIG. 6 The arrangement shown in FIG. 6 is similar to the embodiment illustrated in FIG. 1, corresponding parts being denoted by the same reference numerals.
  • the supply pressure line 1 opens through the lower seat member 2 into the high pressure area 3.
  • the throttling disc 4 which is movable at right angles to the stationary seat member 2, determines the control throttling gap and the load throttling gap 6.
  • the control, or intermediate, pressure area is denoted by the numeral 7 and the load pressure area by the numeral 8.
  • the throttling disc 4 is enclosed in the housing 9.
  • a threaded opening 17 enables a suitable valve to be screwed into the housing 9, as required.
  • the mouth of the high pressure line is denoted by the numeral 12 and that of the load pressure line by numeral 13. In the embodiment shown in FIG.
  • a wall forming the control throttling seat 19 is located radially within a wall forming the load throttling seat 14, which makes it necessary to separate the load pressure area 8 from the control pressure area 7 by an elastic, deformable sealing means constructed as a bellows 16.
  • the servo loop resistance owing to the shortest possible sealing length, is automatically a multiple of the load loop resistance, which enables a substantially simpler construction of the labyrinthine wall that increases the length of the seal. Even an annular load throttling seat 14 gives good amplification.
  • the equivalent system for this embodiment is made up of conventional components that would act in a way similar to the amplifier.
  • the control throttling gap 5 is represented by an adjustable throttle 5 and the load throttling gap 6 by an adjustable throttle 6, these two throttles being operated by a differential jack 4'.
  • the electronic equivalent of this system is the bipolar transistor, the opening 17 corresponding to the base, the load pressure line mouth 13 to the emitter, and the feed line 1 to the collector.
  • FIG. 7 is similar to that shown in FIG. 6, although the control throttling gap 5 can be varied by shifting the control throttling seat 19 with a screw 20. This enables a part of the control flow to be withdrawn from the throttling action of the throttling disc 4, which means that the load loop is sealed closed when the control flow falls below a certain value. Consequently, by interposition of the amplifier, a control member that does not completely shut off, such as a flapper valve, can completely close off a load loop at the quiescent flow.
  • a control member that does not completely shut off such as a flapper valve
  • This supplementary control is represented in the equivalent system by a throttle 5" shunted across the controlled throttle 5.
  • the setting of the throttle 5" is controlled externally, such as by a screw 20.
  • FIG. 8 corresponds generally to the fundamental embodiment illustrated in FIG. 6, but additional elastic seals, in the form of bellows, so divide up the pressure areas that the position of the throttling disc is made independent of the load pressure.
  • the upper face of the throttling disc 4 is subject to the control pressure, and the lower face of the disc is divided by bellows seals 23 and 24 into two areas: the previously described high pressure area 3 and an area 25 that is kept pressure-free by a vent 21. Consequently, the control pressure works only against the supply pressure, and the servo loop is completely sealed from the load loop.
  • the load pressure in the space 26, which pressure must be throttled is led by a passage 27 to a compensating space 28, which exists between the bellows 16 and 22.
  • Some fluid other than that in the servo loop can be controlled in the load loop between the lines 1a and 13a. If the load loop is removed, the arrangement can be used as a very low output impedance pressure divider, since the feed pressure of line 1 is divided only as a function of the pressure acting on the throttling disc at the opening 17.
  • the servo loop divides the load pressure by a constant ratio independent of the control flow.
  • the equivalent system clearly shows how the throttling disc is made insensitive to the load pressure by eliminating feedback of the load pressure to the differential jack 4', and by completely separating the servo and load loops by means of separate lines 1 and 17, on the one hand, and 1a and 13a, on the other.
  • FIG. 9 The arrangement illustrated in FIG. 9 is based upon that illustrated in FIG. 8, and shows a plurality of load loops controlled by a single servo loop. To this end, a plurality of bellows seals and a plurality of lines la, lb, and 1c and 13a, 13b, and 13c are provided. In order to prevent the load loops from reacting on the throttling disc, all pressures acting on one face of the disc must be compensated for on the opposite face.
  • the three load loops are controlled by the valves 6a, 6b, and 6c.
  • the manner of operation of the two series-connected amplifiers is not different from that of the individual members. It should be observed that the supply pressure of amplifier A is the same as the intermediate pressure of amplifier B. The consequence of this is that the supply pressure line 1A of amplifier A and the opening 178 of amplifier B are one and the same, and that the lower seat member 2A of amplifier A is identical with the housing 9B of amplifier B.
  • the vent for the pressurefree area 25B, the control flow of the viscothermic throttle, and the load flow of amplifier A are returned to the tank (not shown) by a collecting line 34.
  • the effective load connection is the load pressure line 13aB of amplifier B.
  • the throttling at the opening 17A is ensured by a viscothermic throttle consisting of an electrically heated resistance wire 29, which is held coaxially in a bore of a throttle body 30 by the housing 9 A and a terminal holder 32. The whole is held in a recess of the housing 9A by a setscrew 33, which is electrically isolated from the terminal holder 32 by an insulating plate 31.
  • a viscothermic throttle consisting of an electrically heated resistance wire 29, which is held coaxially in a bore of a throttle body 30 by the housing 9 A and a terminal holder 32.
  • the whole is held in a recess of the housing 9A by a setscrew 33, which is electrically isolated from the terminal holder 32 by an insulating plate 31.
  • control flow which is regulated by changing the hydraulic resistance of the bore in the body 30 by varying the viscosity of the flow, by electrical heating is extremely small.
  • the flow is accordingly increased by the amplifiers A and B.
  • a hydrostatic flow-amplifier with a poppet valve as the throttling means comprising housing means defining a space; a throttling disc forming the poppet of said valve; said disc being received in said space and being reciprocal therein, said disc defining with said housing a first pressure area, a second pressure area, and a third pressure area, first intake means communicating with said first pressure area; outlet means communicating with said second pressure area, second intake means communicating with said third pressure area; a first seat for said disc formed in said housing, said seat separating said first and third pressure areas; a second seat for said disc formed in said housing, said second seat including an annular surface concentric with said first seat and separating said first and second pressure areas, said first and second seats confronting the same side of said disc, control means for establishing effective positions of displacement of said disc simultaneously with respect to said first and second seats, said control means including a source of fluid at adjustable reference pressure, passage means connecting said source and said second intake means of said third pressure area, adjustable valve means disposed intermediate said source and said third pressure area
  • hydrostatic flow-amplifier as defined in claim 4, including a plurality of said elastic seals on each side of said throttling disc for enabling one said servo loop to control a plurality of said load loops.
  • valve means is a viscothermic throttle, and including an electric resistance wire arranged coaxially in the opening of said valve means for electrically heating the fluid of the control flow to change its viscosity in order to regulate the hydraulic resistance of said throttle.
  • hydrostatic flow-amplifier as defined in claim 11, and further including a second hydrostatic flowamplifier connected in series.
  • a hydrostatic flow-amplifier with a poppet valve as the throttling means comprising housing means formed with an axially extending cylinder; a throttling disc forming the poppet of said valve, said disc being received in said cylinder and axially reciprocable therein, said disc including an axial bore and defining with said housing a first pressure area, a second pressure area, and a third pressure area, intake means communicating with said first pressure area and defining a first force-transmitting path; outlet means communicating with said second pressure are and defining a second force-transmitting path; intake means communicating with said third pressure area and defining a third forcetransmitting path; a first seat for said disc formed in said housing coaxial with said axial bore of said disc, said seat separating said first and said third pressure area; a second seat for said disc formed in said housing, said second seat including an annular surface concentric with said first seat and separating said first and said second pressure areas, said first and said second seat confronting the same side of said disc, control means for establishing

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Fluid Pressure (AREA)
  • Servomotors (AREA)
  • Safety Valves (AREA)
  • Temperature-Responsive Valves (AREA)
US82847669 1968-06-27 1969-05-28 Hydrostatic flow-amplifier Expired - Lifetime US3842855A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH961668A CH492886A (de) 1968-06-27 1968-06-27 Hydrostatischer Stromverstärker
CH1619468A CH501844A (de) 1968-06-27 1968-10-30 Hydrostatischer Stromverstärker

Publications (1)

Publication Number Publication Date
US3842855A true US3842855A (en) 1974-10-22

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ID=25705056

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Application Number Title Priority Date Filing Date
US82847669 Expired - Lifetime US3842855A (en) 1968-06-27 1969-05-28 Hydrostatic flow-amplifier

Country Status (6)

Country Link
US (1) US3842855A (de)
CH (1) CH501844A (de)
DE (1) DE1927883C3 (de)
FR (1) FR2016777B1 (de)
GB (1) GB1277641A (de)
SE (1) SE353136B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4593715A (en) * 1983-12-02 1986-06-10 Glyco-Antriebstechnik Gmbh Hydraulic controllable two-port valve for a liquid stream

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1346233A (fr) * 1962-02-07 1963-12-13 Siemens Ag élément pneumatique de commande
FR1377079A (fr) * 1962-12-13 1964-10-31 Siemens Ag Commutateur ou amplificateur pneumatique ou hydraulique
FR1442588A (fr) * 1965-05-18 1966-06-17 Honeywell Inc Amplificateurs à fluide

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4593715A (en) * 1983-12-02 1986-06-10 Glyco-Antriebstechnik Gmbh Hydraulic controllable two-port valve for a liquid stream

Also Published As

Publication number Publication date
SE353136B (de) 1973-01-22
FR2016777A1 (de) 1970-05-15
DE1927883C3 (de) 1975-07-10
DE1927883A1 (de) 1970-01-15
CH501844A (de) 1971-01-15
DE1927883B2 (de) 1972-06-29
GB1277641A (en) 1972-06-14
FR2016777B1 (de) 1973-10-19

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AS Assignment

Owner name: GLYCO-ANTRIEBSTECHNIK GMBH, STIELSTRASSE 18, D-62

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:CYPHELLY, IVAN J.;REEL/FRAME:004224/0085

Effective date: 19840124