US3863546A - Control valve and fluid motor arrangement - Google Patents

Control valve and fluid motor arrangement Download PDF

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Publication number
US3863546A
US3863546A US363338A US36333873A US3863546A US 3863546 A US3863546 A US 3863546A US 363338 A US363338 A US 363338A US 36333873 A US36333873 A US 36333873A US 3863546 A US3863546 A US 3863546A
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United States
Prior art keywords
oil
spindle
pulley
actuating mechanism
control 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
Application number
US363338A
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English (en)
Inventor
Youichi Saida
Hajime Ito
Kojiro Imanaga
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.)
Mitsubishi Metal Corp
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Mitsubishi Metal Corp
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Filing date
Publication date
Priority claimed from JP6248372U external-priority patent/JPS536094Y2/ja
Priority claimed from JP6248472U external-priority patent/JPS5245756Y2/ja
Application filed by Mitsubishi Metal Corp filed Critical Mitsubishi Metal Corp
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Publication of US3863546A publication Critical patent/US3863546A/en
Assigned to MITSUBISHI KINZOKU KABUSHIKI KAISHA reassignment MITSUBISHI KINZOKU KABUSHIKI KAISHA CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: MITSUBISHI KINZOKU KOGYO KABUSHIKI KAISHA, 6, OTEMACHI 1-CHOME, CHIYODA-KU, TOKYO-TO
Assigned to MITSUBISHI MATERIALS CORPORATION reassignment MITSUBISHI MATERIALS CORPORATION CHANGE OF ADDRESS Assignors: MITSUBISHI KINZOKU KABUSHIKI KAISHA, 5-2, OTEMACHI 1-CHOME, CHIYODA-KU, TOKYO-TO
Assigned to MITSUBISHI MATERIALS CORPORATION reassignment MITSUBISHI MATERIALS CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: MITSUBISHI KINZOKU KABUSHIKI KAISHA, 5-2, OTEMACHI 1-CHOME, CHIYODA-KU, TOKYO-TO
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Expired - Lifetime legal-status Critical Current

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    • 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
    • F16K11/08—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks
    • F16K11/085—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with cylindrical plug
    • F16K11/0856—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks with cylindrical plug having all the connecting conduits situated in more than one plane perpendicular to the axis of the plug
    • 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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/14—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with rotary servomotors
    • 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
    • F16K11/078—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 pivoted and linearly movable closure members

Definitions

  • ABSTRACT A control valve for a rotary type hydraulic servoactuating mechanism comprising a hollow casing having therewithin a valve portion and a manifold portion, pressurized oil feeding and discharging ports communicated with the valve portion, a spindle slidably and rotatably mounted in the: hollow casing, and a pair of oil paths axially formed in the spindle and communicated with long grooves open to the valve portion in the hollow casing.
  • the valve is further provided with means to feed back thereto the motion derived from the servo-actuating mechanism.
  • a CONTROL VALVE AND FLUID MOTOR ARRANGEMENT This invention relates to a control valve, and, more particularly, it is concerned with a hydraulic type control valve which is actuated by rotary motion, linear motion, and a composite motion of the abovement-ioned two motions to be imparted thereto, and further provided with a feedback mechanism, by which the motion derived from a hydraulic servo-actuating mechanism is fed back to the control valve.
  • a control valve comprising in combination a hollow casing provided at a position adjacent to one end thereof with a section defining a valve portion, and provided at a position adjacent to the opposite end thereof with a section defining a manifold portion, a pressurized oil feeding port and a pressurized oil discharging port, both being connected to said valve portion, a spindle concentrically mounted in said hollow casing in a freely slidable and rotatable manner, and a pair of oil paths axially formed within said spindle and extending from said valve portion upto said manifold portion, said oil paths bored in said spindle being each provided with a long groove open to said valve portion in said hollow casing.
  • a control valve further including a feed back mechanism constructed with a pair of pulleys and an endless belt tensioned thereon.
  • FIG. I is a view in longitudinal cross-section showing one embodiment of the control valve according to the present invention.
  • FIG. 2A is a side view of the spindle for use in the control valve shown in FIG. 1;
  • FIG. 2B is a cross-sectional view of the spindle taken along the plane indicated by a line 2B-2B in FIG. 2A;
  • FIG. 2C is a cross-sectional view of the spindle taken along the plane indicated by a line 2C-2C in FIG. 2A;
  • FIG. 3 is a cross-sectional view of the valve section ofthe device shown in FIG. 1 taken along the plane indicated by a line lII-IIl;'
  • FIG. 4 is a longitudinal cross-section showing a modification of the control valve mechanism shown in FIG. 1;
  • FIG. 5 is a cross-sectional view showing the control device in FIG. 4 taken along the plane indicated by a line VV;
  • FIG. 6 is a side elevational view of a bush for use in the device shown in FIG. 1;
  • FIG. 7 is a cross-sectional view of the bush shown in FIG. 6 taken along the plane indicated by a line VII- -VII;
  • FIG. 8 is a side view in longitudinal cross-section showing another embodiment of the control valve according to the present invention.
  • FIG. 9 is a cross-sectional view of the valve section of the device shown in FIG. 8 taken along the plane indicated by a line IX-IX;
  • FIG. 1.0 is a cross-sectional view of the feedback mechanism provided in the device shown in FIG. 8 taken along the plane indicated by line X-X.
  • the servocontrol valve 10 is constructed with a hollow casing I provided therein with a pressurized oil feeding port 5 and a pressurized oil discharging port 6, and a spindle 3 provided therein with a pair of internal oil paths 7 and 8 bored mutually in parallel in the axial direction thereof and mounted oil-tight in the casing l.
  • the casing 1 in one half thereof (e.g., left side), is provided with a section defining a valve portion 25, and, in its remaining half part (e.g., right side), with a section defining a manifold portion 4.
  • this manifold portion 4 consists of two chambers of 4A and 4B, each of which is connected to a desired hydraulic rotary servo mechanism, e.g., hydraulic actuating chambers on both sides of the hydraulic actuating cylinder through appropriate pipings (not shown) to be fitted to the respective connecting port 22 or 23.
  • the spindle 3 performs not only relative rotational movement with respect to the casing l, but also linear movement in the axial direction thereof as it is mounted oil-tight in the casing I in a slidable manner.
  • One of the oil paths bored within the spindle in its axial direction is open at its one end (the left end in the drawing) to the valve portion 25 situated beneath the pressurized oil feeding port 5, and, at its other end (the right end in the drawing) to the left oil chamber 4A of the manifold portion 4.
  • the other oil path 8 is open at its one end (the left end in the drawing) to the valve portion 25, and, at its the other end (the right end in the drawing) to the left oil chamber 48 of the manifold portion 4.
  • These oil paths 7 and 8 are communicated to the valve portion 25 by means of radially extending oil paths 7A and 8A, respectively, which in turn communicate with long grooves 31 and 32 respectively formed on the outer periphery of the spindle 3.
  • Each of the oil paths 7 and S, the pressurized oil feeding port 5 and the pressurized oil discharging port 6 are so arranged interrelatedly that, when the oil path 7 is connected to the pressurized oil feeding port 5 through the long groove 31, the oil path 8 is communicated with the pressurized oil discharging port 6, and, conversely, when the oil path 7 is connected to the pressurized oil discharging port 6, the oil path 8 is communicated with the pressurized oil feeding port 5.
  • the long grooves 31, 32 are in spiral form as shown in FIG. 2A.
  • the pressurized oil feeding port 5 of the casing l is connected to an oil port 34 ofa bore 33 formed in the casing I through a radially extending passage 5A, and the pressurized oil discharging port 6 is connected to two oil ports 35 and 36 of the bore 33 through a radially extending passage 6A and an arcuate passage 68.
  • the oil ports 34, 35 and 36 of the casing l and the long grooves 31 and 32 formed on the outer periphery of the spindle 3 are so interrelatedly disposed that, when the spindle 3 is rotated clockwise from its neutral position as shown in FIG. 3, the long grooves 31 and 32 respectively meet with the oil ports 34 and 36 of the casing 1, and, conversely, when the spindle 3 is rotated in the counterclockwise direction, the long grooves meet with the oil ports 35 and 34, respectively.
  • pressurized oil in the ri g ht oil chamber 48 of the manifold 4 is discharged from and oil discharging port 6 through the oil paths 8 and 8A, long groove 32, oil port 36, arcuate passage 68, and radially extending passage 6C.
  • FIG. 4 is a modification of the control valve shown in FIG. I, in which a bush 2 is fixedly mounted at the left end of the casing l.
  • the inner surface of the bush 2 is oil-tightly contacted with the outer periphery of the spindle 3.
  • the bush 2 is provided on its outer periphery with three spiral, long grooves 11, 12, and 13.
  • the middle groove 12 is communicated with the pressurized oil feeding port 5, and the other grooves 11 and 13 are communicated with the pressurized oil discharging port 6 through the oil paths 6A and 6B.
  • FIG. 5 indicates that the spindle 3 of the control valve path is in a neutral position.
  • the spiral long groove 12 meets with the oil path 8A, and the pressurized oil feeding port 5 becomes communicated with the right oil chamber 48 of the manifold portion 4 through the oil paths 8A and 8, whereby oil is poured into the oil chamber 48.
  • the spiral grooves 11 meets with the oil path 7A, and the pressurized oil discharging port 6 becomes communicated with the left oil chamber 4A of the manifold portion 4 through the oil path 6A, groove 11, and oil paths 7A and 7, whereby the oil in the oil chamber 5 4A is discharged.
  • Feeding and discharging of the pressurized oil to and from both oil chambers 4A and 4B of the manifold portion 4 result in the feeding and discharging of oil to and from a hydraulic servo-actuating mechanism.
  • oil chambers on both sides of a piston in a hydraulic cylinder for example, oil chambers on both sides of a piston in a hydraulic cylinder.
  • the spindle 3 is connected to a rotary input source 14 such as a pulse motor by way of a spline 9 fitted at the extreme left end of the spindle.
  • the numeral 14A designates a sleeve with spline as fitted to the pulse motor 14.
  • the spindle 3 is con nected to' a shifting lever 17 for shifting the spindle in its axial direction through a collar 15 and a connecting rod 16.
  • the connecting rod 16 is mounted on the collar 15 in a freely rotatable manner at its one end, and is fixed to the shifting lever 17 at its other end.
  • the shifting lever 17 is held by supporting members 18 and 19 in a freely slidable manner, while it is constantly pressed leftward by force of a spring 21.
  • the shifting lever 17 can be adjusted in the axial direction by an adjusting screw 20.
  • FIG. 8 shows another embodiment of the control valve according to the present invention
  • a pulley 30 at the left end of the casing 1 of the control valve 10, and, adjacent to this pulley 30, there is disposed another pulley 28 which is mounted on and supported by a rotary shaft 27 for a rotary type hydraulic actuating mechanism.
  • Both pulleys 28 and 30 are joined by an endless belt 29 tensioned therebetween.
  • the pulley 30 is driven by the revolution of the pulley 28 through the belt 29.
  • This additional mechanism functions to feed back to the control valve the motion of the rotary type hydraulic actuating mechanism 26 which is driven by the control valve per se.
  • the casing 1 performs a following rotation by way of the pulley 28, belt 29, and pulley 30 in response to the rotational quantity so as to reinstate the original neutral state of the casing l and the spindle 3 as shown in FIG. 9 from their relative positional relationship caused by the rotation, to offset the output of the control valve, and to cause the rotary type hydraulic actuating mechanism 26 to stop at its rotated position. Accordingly, in proportion to the rotational displacement ofthe pulse motor 14, there can be obtained an output rotational displacement on the hydraulic actuating mechanism.
  • control valve according to the present invention is capable of being actuated by the rotary input source 14 and the linear input source 17 as well, and, moreover, it can be actuated by a composite motion of the rotary and linear motions.
  • control valve according to the present invention is so designed that the manifold portion 4 is connected to a desired hydraulic actuating mechanism by means of an appropriate piping, there is no inconvenience to take place at all, even when the control device needs be installed at a location remote from the actuating mechanism.
  • the hydraulic actuating mechanism is actuated in accordance with the oil feeding and discharging to and from the manifold portion, the motion of which is fed back to the casing 1.
  • a control valve for a rotary type hydraulic servoactuating mechanism comprising a. a hollow casing with a portion of one end defined as a valve portion, and at the other end a portion defined as ,a manifold portion, said manifold portion having passage means adapted to be connected to the hydraulic servo-actuating mechanism, and said casing further having in the valve portion a pressurized oil feeding port and a pressurized oil discharging port, and
  • a spindle concentrically mounted insaid hollow 2.
  • a'feedback mechanism comprising a. a first pulley fitted on one end of said hollow casing, b. a rotary shaft adapted to be: driven by the rotary type hydraulic servo-actuating mechanism,
  • said second pulley being disposed in alignment with said first pulley

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Multiple-Way Valves (AREA)
US363338A 1972-05-27 1973-05-24 Control valve and fluid motor arrangement Expired - Lifetime US3863546A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP6248372U JPS536094Y2 (ja) 1972-05-27 1972-05-27
JP6248472U JPS5245756Y2 (ja) 1972-05-27 1972-05-27

Publications (1)

Publication Number Publication Date
US3863546A true US3863546A (en) 1975-02-04

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ID=26403524

Family Applications (1)

Application Number Title Priority Date Filing Date
US363338A Expired - Lifetime US3863546A (en) 1972-05-27 1973-05-24 Control valve and fluid motor arrangement

Country Status (5)

Country Link
US (1) US3863546A (ja)
CA (1) CA978049A (ja)
FR (1) FR2189669B1 (ja)
GB (1) GB1415433A (ja)
IT (1) IT990591B (ja)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4092990A (en) * 1975-09-15 1978-06-06 Standard Changemakers, Inc. Vibratory coin feeder
WO2002029255A1 (en) * 1999-04-12 2002-04-11 Kenneth Edlund Fluid-activated adjustment and manoeuvre device
US6417640B1 (en) * 1999-07-16 2002-07-09 Lucas Aerospace Fcs Displacement sensors for servo-control actuators
US20070037502A1 (en) * 1998-02-23 2007-02-15 Clayton R P System for reducing microbial levels on the hide of an animal
EP3388722A1 (de) * 2017-04-13 2018-10-17 Continental Automotive GmbH Fluidventil aufweisend einen ersten körper und einen zweiten körper

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2189053A (en) * 1986-02-22 1987-10-14 Robert Colin Pearson Motor systems
EP2101092A1 (de) * 2008-03-11 2009-09-16 Qiagen GmbH Flüssigkeitssteuerungseinrichtung für Mikrodurchflusssystem

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2132486A (en) * 1935-08-22 1938-10-11 Messerschmitt Boelkow Blohm Control of fluid-operated pistons
US2398586A (en) * 1944-01-01 1946-04-16 H M Hobson Aircraft & Motor Co Power control for aircraft engines
US2521557A (en) * 1948-04-07 1950-09-05 Chrysler Corp Apparatus for successively making approximate and final adjustments
US3079899A (en) * 1959-05-29 1963-03-05 Fuji Tsushinki Seizo Kk Feedback-type oil-hydraulic drive
US3125002A (en) * 1964-03-17 Input

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE706193C (de) * 1935-08-23 1941-05-20 Messerschmitt Boelkow Blohm Durch ein Druckmittel zu betreibende Verstellvorrichtung
US2874542A (en) * 1943-04-21 1959-02-24 Sperry Rand Corp Motion reproducing mechanism
FR1372718A (fr) * 1963-08-28 1964-09-18 Bolkow Entwicklungen Kg Mécanisme hydraulique à commande assistée

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125002A (en) * 1964-03-17 Input
US2132486A (en) * 1935-08-22 1938-10-11 Messerschmitt Boelkow Blohm Control of fluid-operated pistons
US2398586A (en) * 1944-01-01 1946-04-16 H M Hobson Aircraft & Motor Co Power control for aircraft engines
US2521557A (en) * 1948-04-07 1950-09-05 Chrysler Corp Apparatus for successively making approximate and final adjustments
US3079899A (en) * 1959-05-29 1963-03-05 Fuji Tsushinki Seizo Kk Feedback-type oil-hydraulic drive

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4092990A (en) * 1975-09-15 1978-06-06 Standard Changemakers, Inc. Vibratory coin feeder
US20070037502A1 (en) * 1998-02-23 2007-02-15 Clayton R P System for reducing microbial levels on the hide of an animal
WO2002029255A1 (en) * 1999-04-12 2002-04-11 Kenneth Edlund Fluid-activated adjustment and manoeuvre device
US6417640B1 (en) * 1999-07-16 2002-07-09 Lucas Aerospace Fcs Displacement sensors for servo-control actuators
EP3388722A1 (de) * 2017-04-13 2018-10-17 Continental Automotive GmbH Fluidventil aufweisend einen ersten körper und einen zweiten körper

Also Published As

Publication number Publication date
GB1415433A (en) 1975-11-26
IT990591B (it) 1975-07-10
FR2189669A1 (ja) 1974-01-25
FR2189669B1 (ja) 1976-05-07
CA978049A (en) 1975-11-18

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AS Assignment

Owner name: MITSUBISHI MATERIALS CORPORATION, JAPAN

Free format text: CHANGE OF ADDRESS;ASSIGNOR:MITSUBISHI KINZOKU KABUSHIKI KAISHA, 5-2, OTEMACHI 1-CHOME, CHIYODA-KU, TOKYO-TO;REEL/FRAME:005822/0501

Effective date: 19881128

Owner name: MITSUBISHI KINZOKU KABUSHIKI KAISHA

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Effective date: 19910313

Owner name: MITSUBISHI MATERIALS CORPORATION

Free format text: CHANGE OF NAME;ASSIGNOR:MITSUBISHI KINZOKU KABUSHIKI KAISHA, 5-2, OTEMACHI 1-CHOME, CHIYODA-KU, TOKYO-TO;REEL/FRAME:005797/0028

Effective date: 19910222