US3905275A - Hydraulic control valve for rotary servo-mechanism - Google Patents

Hydraulic control valve for rotary servo-mechanism Download PDF

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Publication number
US3905275A
US3905275A US354882A US35488273A US3905275A US 3905275 A US3905275 A US 3905275A US 354882 A US354882 A US 354882A US 35488273 A US35488273 A US 35488273A US 3905275 A US3905275 A US 3905275A
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Prior art keywords
input shaft
oil
output shaft
casing
shaft
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Expired - Lifetime
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US354882A
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English (en)
Inventor
Youichi Saida
Hajime Ito
Kojiro Imanaga
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Mitsubishi Metal Corp
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Mitsubishi Metal Corp
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Priority claimed from JP4224372A external-priority patent/JPS493093A/ja
Priority claimed from JP4224472A external-priority patent/JPS493073A/ja
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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
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 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
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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
    • 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
    • F15B9/02—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 servomotors of the reciprocatable or oscillatable type
    • F15B9/08—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 servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/10—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 servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor in which the controlling element and the servomotor each controls a separate member, these members influencing different fluid passages or the same passage
    • 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

Definitions

  • a gg gt f g Pnonty Data an output shaft integrally formed with a rotor, wherein the inner surface of of the annular casing and the outer surface of the rotor are shaped to define a plurality of oil chambers in conjunction with partition walls provided on the annular casing and the rotor.
  • FIGQIIb PATENTED SEP I 6 I975 SHEET HYDRAULIC CONTROL VALVE FOR ROTARY SERVO-MECHANISM
  • This invention relates to a hydraulic control valve, or, more particularly, it is concerned with a hydraulic control valve for a rotary servo-mechanism which performs not only relative rotational movement between the input shaft and the output shaft, but also relative reciprocal movement in the axial direction between the input and output shaft.
  • FIG. 1 is a-Iongitudinal crosssection showing a hydraulic rotary servo-mechanism, in which the hydraulic control valve according to the present invention is provided;
  • FIG. 2a is a cross-sectional view of theservo mechanism shown in FIG. 1 above taken along the plane II- FIG. 2b is a cross-sectional view of a modified construction thereof;
  • FIGS.- 3a ancl 3b are schematic diagrams showing connections of the feeding and discharging system for the device shown in FIG. 2, in which FIG.3a is for clockwise rotation of the rotor, and FIG. 3b'is for coun-
  • FIG. 9 is a longitudinal cross-section showing another embodiment of the rotary servo-mechanism according to the present invention.
  • FIGS. 10a and 10b show the detailed construction of the input shaft of the device shown in FIG. 9;
  • FIGS. 11a and 11b are details of the construction of the piston rod used in the device shown in FIG. 9;-
  • FIG. 12 is' a longitudinal cross-sectionof'a'further embodiment of the servo-mechanism according to the present invention.
  • FIGS. 13a and 13b show details of the'construction of the pistonrod used in the device shown in FIG. 12, and
  • FIGS. 14a and 14b show details of the structure of the sleeve used in the device shown in FIG. 12.
  • the device has an annular casing l, and input shaft 4 and an output shaft 6, both of which pass through the center part of the annular casing 1 axially thereof.
  • the annular casing l is tightly sealed by the end walls 2 and 3 fitted at both ends of the casing.
  • a rotor 5 is integral with the ou'tput shaft 6 within'the annular casing. More specifically, the rotor 5 is provided on its inner surface with a gun metal liner 7 which maintains smooth rotation of the rotor and output shaft 6 around the outer periphery of the input shaft 4 along with oil-tightnesstherebetween.
  • the output shaft 6 is also mounted on the outer periphery of the input shaft 4 throughrthe liner 7.
  • the annular casing 1 is provided with a pair of partition walls 12 and 13 which project inwardly to the center part of the casing.
  • the rotor 5 is provided with a pair of outwardly extending wings 9 and 10 positioned at equal intervals therearound.
  • the extreme end of each of the extended wings is provided with a sealing material to enable the outwardly extending wings. 9 and-10 to oil-tightly. contact with and to be freely slidable along the inner peripheral surface of the annular casing.
  • the partition walls 12 and 13 oil-tightly. contact the outer periphery of the rotorsrAlthough, in this embodiment of FIG.
  • passages 23a, 23b, 24a, and 24b are respectively connected to the hydraulic actuating chambers 25, 26, 27, and 28.
  • the annular pas- I sages 23 and 24, for pressurized oil are opposed to the oil ports 21 and 22, respectively, in sleeve 7.
  • the end wall 3 is provided with an oil feeding passage 31 communicating with a pressurized oil feeding source S and an oil discharging passage communicating with an oil discharging vessel T.
  • Both passages 31 and 32 are respectively connected to another pair of annular oil passages 33 and 34 surrounding the outer periphery of the input shaft 4.
  • the oil feeding port 18 and the oil discharging ports 19 and 20 radially formed within the input shaft and extending to the outer periphery thereof, and the oil ports 21 and 22 provided in the sleeve 7 constitute a control valve 101 for the hydraulic rotary servo-mechanism 100.
  • FIG. 2b is a modification of FIG. 2a, in which each of four partition members provided in the annular casing 1 is movably mounted for movement back and forth toward the center axis of the annular casing, and three partition membersare provided on the rotor each being in the form of a wedge-shaped projection. Except for this particular construction of the partition members, the construction of the control valve 101 is exactly same as that in FIG. 2a.
  • the pressurized oil feeding passage 16 of the inlet shaft 4 communicates with the oil port 21 of the sleeve 7, while the pressurized oil discharging passage 17 communicates with the oil port 22. Accordingly, pressurized oil is fed into the chambers 26, 28 and 30, and discharged from the chambers 25, 27, and 29 with the consequences that the rotor 5, and hence the output shaft 6, rotates in the clockwise. direction. Conversely,.;when the input shaft 4 is caused to rotate in the counter-clockwise direction from its neutral position in FIG. 2b, and the control valve 101 is brought to a position as shown in FIG.
  • the pressurized oil feeding passage 16 of the input shaft communicates with the oil port 22 of the rotor 5, while the pressurized oil discharging passage 17 communicates with the oil port 21 of the rotor with' the consequence that the oil is fed into the chambers 25, 27, and 29, and discharged out of the chambers 26, 28, and 30, hence the rotor 5 (and output shaft 6) rotates in the counter-clockwise direction.
  • the oil ports for feeding and discharging pressurized oil can be provided in either the input shaft 4 or the sleeve 7 constituting the control valve 101 and are formed in such a manner that each of them is a long groove which runs obliquely'with respect to the center line of the inputshaft 4 at the sliding surface between the outer surface of the input shaft 4 and the inner surface of the sleeve 7, and that the input shaft 4 is slidable in the axial direction with respect to the rotor 5.
  • FIGS. 4a-4e show one embodiment of the constructionof the controlvalve according to the present invention, in which the oil ports 21 and 22 formed in the gun metal liner 7 on the inner surface of the rotor are long grooves which run obliquely with respect to the center axis X-X of the input shaft 4.
  • the oil ports 21 and 22 are formed substantially spirally in the liner 7 which has a tubular shape, although they can be v formed in curved forms other than spiral depending on necessity.
  • the pressurized oil discharging port 19 or 20 can be made to register with or be spaced from the oil ports 21 and 22, even if the input shaft 4 is shifted in the axial direction with respect to'the rotor 5; In other words, by the" back-and-forth movement of the input shaft 4 in the axial direction thereof, it is possible to open or close the control valve 101. Consequently, the control valve 101 according to the presentinvention is responsive to various input motions such as rotational motion, linear motion, or composite motion of the two.
  • FIGS. 5a-5g show a modification of the control valve shown in FIGS. 4a, 4b, and 40 above, wherein a pres surized oil feeding port 18 and pressurized oil discharging ports 19 and 20 are provided in a spiral form on the outer surface of the input shaft 4, while ordinary circular ports 21 and 22 are formed in the inner surface of the liner 7.
  • the operating principle is exactly same as that in the embodiment shown in FIGS. 40, 4b, and 4c.
  • FIGS. 6a-6e show still another modification of the control valve according to the present invention, wherein the liner 7 is in contact with the input shaft 4 as an input member which is freely rotatable and freely slidable in the axial direction, and a spiral oil feeding port 21 and spiral oil discharging ports 22 and 22a are formed in the liner 7.
  • FIGS. 7a-7e show a further modification of the control valve according to the present invention, wherein the liner 7 is used as the input member, while the shaft 4 is fixed, and in which the spiral oil feeding port 18 and the spiral oil discharging port 19 are formed.
  • FIG. 8 shows another embodiment of the hydraulic rotary servo-mechanism having the hydraulic control valve according to the present invention.
  • the inner surface of the annular casing has a substantially oval shape in cross-section and a plurality of partition members 9A through 9N are fitted on the rotor in a freely, outwardly and inwardly slidable manner. These partition members are urged outwardly in the radial direction by spring force exerted by springs 35A through 35N for each partition member.
  • the construction of the control valve 101 provided in the center axis of this servo-mechanism is also exactly same as those explained in the foregoing.
  • a hydraulic servo-actuator 50 of the present invention consists of a hydraulic cylinder 1, a cylindrical casing 4 integrally and concentrically formed with the hydraulic cylinder 1, apiston 2 which is accommodated within the hydraulic cylinder 1 and is freely slidable along the inner periphery of the hydraulic cylinder 1, and a piston rod 6 which is integrally formed with the piston 2 and projects outward through an end wall 1A covering one end of the cylinder 1.
  • the cylindrical casing 4 is also closed at its one end opposite the end wall 1A with another end wall 5.
  • the abovementioned piston rod 6 also extends toward the cylindrical casing 4 (i.e., toward the left side of the drawing) and is in oil-tight relationship with the inner wall of the cylindrical casing 4.
  • the piston rod 6 is also provided with a concentric bore 7 therewithin which opens at the left end inside the cylindrical casing 4.
  • the input shaft 3 passes through the opening 20 of the end wall of the cylindrical casing 4 in a freely slidable and rotatable manner.
  • a pressurized oil feeding port 10 connected to an appropriate pressurized oil feeding source (not shown) such as a hydraulic pump, etc., and a pressurized oil discharging port 1 1 connected to a discharge oil vessel (not shown).
  • the pressurized oil feeding port, or oil intake, 10 is further connected to an annular groove 12 formed on the inner surface of the opening 20 of the end wall 5 through an oil passage 10A which is also formed within the end wall 5.
  • the pressurized oil discharge port 11 is connected to another annular groove 13 formed on the inner surface of the opening 20 of the end wall 5 through another oil passage 11A.
  • the input shaft 3 is provided therewithin with a pressurized oil feeding passage 14 and a pressurized oil discharging 15 which are parallel to each other in the axial direction of the input shaft 3.
  • Both pressurized oil feeding passage 14 and pressurized oil discharging passage 15 are respectively connected to the annular groove 12 for oil feeding and the annular groove 13 for oil discharging by way of radially extending passages 14A and 15A.
  • these pressurized oil feeding passage 14 and pressurized oil discharging passage 15 are connected at their other ends (i.e., right side of the sheet of the drawing) with long grooves 16, and 17 and 17a, respectively formed on the outer periphery of the input shaft 3. According to FIG.
  • these long grooves 16, 17, and 17a are formed on the outer periphery of the input shaft in a spiral direction and substantially parallel to each other.
  • the shape of the long grooves is not limited to the spiral form alone, but any other appropriate shape may be chosen depending on the required responsive characteristics of the output shaft 6.
  • the piston rod (output shaft) 6 is provided within its cylindrical wall with mutually parallel oil passages 18 and 19 extending in the axial direction thereof.
  • the oil passage 18 is open at one end thereof to the bore 7 and at the other end to the chamber A on the left side of the piston 2.
  • the oil passage 19 is open at its one end to the bore 7 and at the other end to the chamber B on the right side of the piston 2.
  • the opening 18A of the oil passage 18 and the opening 19A of the oil passage 19 opening into the bore 7 are positioned in such a manner that each of them is circumferentially aligned with the center part of each of the abovementioned long grooves 16, 17, and 17a formed on the outer peripheral surface of the input shaft 3.
  • the long grooves 16, 17, and 17a are connected to the pressurized oil feeding passage 14 and the pressurized oil discharging passage 15, and the oil passages 18 and 19 formed in the cylindrical wall of the piston rod 6, both of which are open to the inner surface of the bore 7, constitute the hydraulic control valve 51 for the servo-actuating mechanism according to the present invention.
  • Both input shaft 3 and piston rod 6 not only rotate mutually along the control valve 51, but also mutually slide in the axial direction.
  • both the long'groove 16 for oil feeding of the input shaft 3 and long grooves 17 and 17a for oil discharging are circumferentially offset from and thus completely disconnected from the two oil passages 18 and 19 formed in the cylindrical wall of the piston rod 6, and there is no flow of the pressurized oil in and out of the two oil chambers within the cylinder, and hence no movement of the output shaft 6.
  • pressurized oil within the left oil chamber A is discharged into the discharge oil vessel through the oil passage 18, long groove 17, oil passage 15, annular groove 13, oil passage 11A, and pressurized oil discharging port 11. Conversely, when the input shaft 3 is moved leftward, the oil passages 18A and 19A are brought into register with the long grooves 16 and 17, respectively.
  • pressurized oil is fed into the left oil chamber A of the cylinder 1 through the pressurized oil feeding port 10, oil passage 10A, annular groove 12, oil passage 14, long groove 16, and oil passage 18, and, at the same time, pressurized oil in the right oil chamber B is discharged into the discharge oil vessel through the oil passages 19, 19A, long groove 17a, oil passage 15, annular groove 13, oil passage 11A, and pressurized oil discharging port 11. Consequently, the output shaft of the piston moves rightward.
  • the pressurized oil is introduced into the left oil chamber A of the piston 2 through the pressurized oil feeding port 10, oil passage 10A, annular groove 12, pressurized oil feeding passage 14, long groove 16, and oil passage 18 of the output shaft.
  • the pressurized oil in the right oil chamber B of the piston 2 is led to the presssurized oil discharging port 11 through the oil passage 19 of the piston rod 6, long groove 17a of the input shaft, pressurized oil discharging passage 15, annular groove 13, and oil passage 1 1A, and it is finally discharged into the discharge oil vessel (not shown). Accordingly, the piston 2 and the output shaft 6 perform linear movement to the right in FIG. 9. Thus, by the operation of the servo-actuating mechanism according to the present invention, the rotational movement of the input shaft 3 is converted into linear movement of the output shaft 6.
  • FIGS. 12, 13a, 13b, 14a and 14b show other embodiments of the present invention, in which the piston rod (output shaft) 6 passes through both ends of the hydraulic cylinder 1 and extends through the entire de vice, and the input shaft 30 is in the form of a sleeve, which is rotatably and oil-tightly mounted on the outer periphery of the piston rod 6.
  • the left end of the oil passages 18 and 19 formed mutually in parallel and in the axial direction of the piston rod 6 are connected to long grooves 41 and 42, respectively.
  • the sleeve 30 is provided at its right end with a flange 31, which in turn is accommodated in an annular groove or cavity 32 formed in the left end of the cylinder 1, whereby the sleeve 30 is rotatably held in the cylinder 1.
  • a pressurized oil feeding passage 33 and a pressurized oil discharging passage 34 extending in the axial direction thereof.
  • the pressurized oil feeding passage 33 is connected at its right end to the pressurized oil feeding port 10 through the oil passage 10A formed within one end wall of the cylinder 1 and the annular groove 35 formed on the outer periphery of the sleeve I 30, and is open at its left end to the inner surface of the sleeve 30 (33A).
  • the pressurized oil discharging passage 34 is connected at its right end to the pressurized oil discharging port 11 through the annular groove 36 of the sleeve 30 and the oil passage 11A in the cylinder 1, and is' open-at its left end to the inner surface of the sleeve by means of two openings 34A and 34B.
  • these openings 33A, 34A and 34B formed within the cylindrical wall of the sleeve 30 and respectively connected to the pressurized oil feeding passage and the pressurized oil discharging passage, and the long grooves 41 and 42 formed on the outer periphery of the piston rod 6 and connected respectively to the oil passages 18 and 19 formed within the piston rod 6 constitute the hydraulic control valve 51 for this embodiment.
  • the operation and performance of the control valve and the piston 2 are exactly same as those of the previously explained embodiments.
  • the input sleeve 30 is confined so that it will not move in the axial direction thereof.
  • this member can be fitted in the cylinder so as to be freely slidable in its axial direction. By so doing, not only the rotational movement of the input member, but also the linear movement thereof in the axial direction can be imparted to the control valve 51, whereby an output responsive to such input can be generated at the output shaft (i.e., piston rod) 6.
  • the left ends of the pressurized oil feeding passage 33 and the pressurized oil discharging passage34 formed within the cylindrical wall of the sleeve 30 are placed in communication with the long groove 21 for oil feeding, and the long grooves 22 and 22a, respectively, as shown in FIG. 6b, which is then connected to the oil passages 18 and 19 provided within the piston rod 6.
  • the present invention makes it possible to perform desired various motions of the output means by appropriately selecting the shape of the long groove to be provided in the input shaft or output shaft which constitute a component part of the control valve according to the present invention.
  • a desired non-linear motion can be obtained at the output.
  • an output responsive to a summation or difference of two input forces can be easily obtained, hence the industrial merit of this particular control valve is considered to be great.
  • a hydraulic servo-actuating mechanism comprising an annular casing having an internal bore with a central axis; a plurality of first partition walls projecting from the inner surface of said bore radially inwardly toward said central axis of the casing; end walls closing the axial ends of said bore; an input shaft extending axially through said bore and rotatably positioned therein for rotation around said central axis, said input shaft having therein hydraulic fluid passages connected to a hydraulic pressure source and to a hydraulic fluid reservoir; an output shaft means rotatably mounted on the outer periphery of said input shaft and having a rotor thereon with a plurality of second partition walls which are wedge-shaped projections integral with said output shaft radially outwardly projecting therefrom with the ends thereof slidingly engaging said inner surface of said casing, said first partition walls being movably mounted in said casing for radial back and forth movement and resiliently urged radially inwardly against the outer perhipheral surface of said output shaft, whereby hydraulic actuation of

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Servomotors (AREA)
US354882A 1972-04-28 1973-04-26 Hydraulic control valve for rotary servo-mechanism Expired - Lifetime US3905275A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP4224372A JPS493093A (fr) 1972-04-28 1972-04-28
JP4224472A JPS493073A (fr) 1972-04-28 1972-04-28

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US3905275A true US3905275A (en) 1975-09-16

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US354882A Expired - Lifetime US3905275A (en) 1972-04-28 1973-04-26 Hydraulic control valve for rotary servo-mechanism

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US (1) US3905275A (fr)
CA (1) CA984703A (fr)
DE (1) DE2321280A1 (fr)
FR (1) FR2182243B1 (fr)
GB (1) GB1394138A (fr)
SE (1) SE394312B (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4241643A (en) * 1977-03-05 1980-12-30 Bendix Westinghouse Limited Power assisted actuating arrangements
US5242150A (en) * 1992-09-30 1993-09-07 The United States Of America As Represented By The Secretary Of The Navy Rotary hydraulic servo or throttle valve
WO2002029255A1 (fr) * 1999-04-12 2002-04-11 Kenneth Edlund Dispositif de manoeuvre et d'ajustement mu par fluide
US20030052292A1 (en) * 2001-09-19 2003-03-20 Tranovich Stephen J. Rotary 2-way servovalve
US20100198129A1 (en) * 2007-06-27 2010-08-05 Gambro Lundia Ab Flow reversing device and fluid treatment apparatus

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105927605A (zh) * 2016-05-31 2016-09-07 东南大学 一种通轴式可旋转液压连接件

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1876104A (en) * 1930-11-29 1932-09-06 Tucker Gilmore Mfg Company Steering mechanism
US2398586A (en) * 1944-01-01 1946-04-16 H M Hobson Aircraft & Motor Co Power control for aircraft engines
US2466415A (en) * 1944-01-03 1949-04-05 Hobson Ltd H M Pressure sensitive capsule and mixture control device embodying the same
US3103209A (en) * 1961-03-10 1963-09-10 Gen Motors Corp Phase adjusting servo mechanism for internal combustion engine and the like
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
FR464891A (fr) * 1912-11-27 1914-04-02 Octave Brotelle Tampon en feutre antiseptisé muni de bandes emplastiques, servant de bandage herniaire
FR988565A (fr) * 1944-01-10 1951-08-29 Pompe volumétrique perfectionnée
FR1117494A (fr) * 1954-12-09 1956-05-23 Bendix Aviat Corp Pompe à fluide

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125002A (en) * 1964-03-17 Input
US1876104A (en) * 1930-11-29 1932-09-06 Tucker Gilmore Mfg Company Steering mechanism
US2398586A (en) * 1944-01-01 1946-04-16 H M Hobson Aircraft & Motor Co Power control for aircraft engines
US2466415A (en) * 1944-01-03 1949-04-05 Hobson Ltd H M Pressure sensitive capsule and mixture control device embodying the same
US3103209A (en) * 1961-03-10 1963-09-10 Gen Motors Corp Phase adjusting servo mechanism for internal combustion engine and the like

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4241643A (en) * 1977-03-05 1980-12-30 Bendix Westinghouse Limited Power assisted actuating arrangements
US5242150A (en) * 1992-09-30 1993-09-07 The United States Of America As Represented By The Secretary Of The Navy Rotary hydraulic servo or throttle valve
WO2002029255A1 (fr) * 1999-04-12 2002-04-11 Kenneth Edlund Dispositif de manoeuvre et d'ajustement mu par fluide
US20030052292A1 (en) * 2001-09-19 2003-03-20 Tranovich Stephen J. Rotary 2-way servovalve
US6808162B2 (en) * 2001-09-19 2004-10-26 Victory Controls, Llc Rotary 2-way servovalve
US20100198129A1 (en) * 2007-06-27 2010-08-05 Gambro Lundia Ab Flow reversing device and fluid treatment apparatus
US8568346B2 (en) 2007-06-27 2013-10-29 Gambro Lundia Ab Flow reversing device and fluid treatment apparatus
US9067027B2 (en) 2007-06-27 2015-06-30 Gambro Lundia Ab Flow reversing device and fluid treatment apparatus

Also Published As

Publication number Publication date
FR2182243B1 (fr) 1976-05-07
DE2321280A1 (de) 1973-11-22
FR2182243A1 (fr) 1973-12-07
CA984703A (en) 1976-03-02
SE394312B (sv) 1977-06-20
GB1394138A (en) 1975-05-14

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