US3799096A - Power transmission - Google Patents

Power transmission Download PDF

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Publication number
US3799096A
US3799096A US00218183A US21818372A US3799096A US 3799096 A US3799096 A US 3799096A US 00218183 A US00218183 A US 00218183A US 21818372 A US21818372 A US 21818372A US 3799096 A US3799096 A US 3799096A
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US
United States
Prior art keywords
actuator
command
rudder
hydraulic
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00218183A
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English (en)
Inventor
R Jeffery
R Breeden
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.)
Vickers Inc
Original Assignee
Sperry Rand Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sperry Rand Corp filed Critical Sperry Rand Corp
Priority to US00218183A priority Critical patent/US3799096A/en
Priority to DE2301622A priority patent/DE2301622C3/de
Priority to FR7301396A priority patent/FR2168375B3/fr
Priority to GB216373A priority patent/GB1411002A/en
Priority to JP732873A priority patent/JPS5320638B2/ja
Priority to SE7300556A priority patent/SE382031B/xx
Application granted granted Critical
Publication of US3799096A publication Critical patent/US3799096A/en
Assigned to SPERRY CORPORATION reassignment SPERRY CORPORATION CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: SPERRY RAND CORPORATION
Assigned to VICKERS, INCORPORATED reassignment VICKERS, INCORPORATED ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SPERRY CORPORATION A DE CORP.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
    • B63H25/06—Steering by rudders
    • B63H25/08—Steering gear
    • B63H25/14—Steering gear power assisted; power driven, i.e. using steering engine
    • B63H25/18—Transmitting of movement of initiating means to steering engine
    • B63H25/22—Transmitting of movement of initiating means to steering engine by fluid means
    • 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
    • F15B9/04—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 varying the output of a pump with variable capacity

Definitions

  • a remote control system for ships rudders includes a hydraulic rudder actuator and a reversible variable displacement pump connected to drive it, the pump displacement being under the control of a hydraulic bridge circuit utilizing a pair of bleed circuits controlled respectively by variable command orifices and variable response orifices.
  • the command orifices are constituted by a pair of summing valves responsive to the algebraic sum (or difference) of the angular displacements of a command actuator on the one hand and the rudder actuator on the other hand.
  • the command actuator is hydraulically driven and electrically controlled by a closed loop servo system including a helm control which may comprise an automatic pilot.
  • the present invention aims to provide an improved ships rudder control system which provides reliable follow-up action at lower cost than previous follow-up systems, which permits the use of simple electric wiring between the bridge and the rudder drive and which avoids imposing shock loads on the system.
  • a ships rudder control system which comprises a hydraulic rudder motor and a reversible variable displacement pump for shifting the motor, means for controlling the pump displacement including a servomotor and a hydraulic bridge having a pair of bleed circuits carrying a continuous small flow of pilot control fluid, command means for varying the resistance in a first portion or portions of the bleed circuits, and response means for varying the resistance in a second portion or portions of the bleed circuits as the pump displacement changes, said command means including a first member movable at command and a second member movable in follow-up motion responsive to shifting of the rudder motor.
  • FIG. 1 is a hydraulic circuit diagram ofa rudder control system incorporating a preferred form of the present invention.
  • FIG. 2 is a hydraulic circuit diagram showing a portion of FIG. 1 ingreater detail.
  • FIG. 3 is a longitudinal cross section of a command actuator incorporated in the system of FIG. 1.
  • FIG. 4 is a cross section on line 4-4 of FIG. 3.
  • FIG. 5 is a cross section on line 5-5 of FIG. 3.
  • FIG. 6 is a cross section on line 6--6 of FIG. 3.
  • FIG. 7 is a fragmentary detail of a portion of the control mechanism.
  • FIG. 1 there is indicated an oscillating paddle motor 10 secured to a rudder post 12 and supplied by hydraulic manifolds 14 and 16. Connected across the latter are a pair of over-load relief valves 18 and a bypass valve 20. The three lobed rotor 22 has an arm 24 connected to a response link 26 for the purpose of repeating the motion of the rudder motor 10 at a point in the control mechanism.
  • FIG. 1 there is shown a duplicate set of power and control devices for alternate stand-by use and only one of them will be described.
  • the manifolds 14 and 16 are supplied through main power lines 28 and 30 and a solenoid operated blocking valve 32 (for manually locking the rudder post) from a reversible variable displacement pump 34 driven by an electric motor 36.
  • a pilot control fluid pump 38 is also driven by the motor 36 and supplies fluid to a solenoid operated command valve 40 through a line 42.
  • a branch 44 supplies pilot control fluid to the displacement regulating mechanism of the pump 34 which is illustrated in more detail in FIG. 2 and which will be described later.
  • the displacement regulating system is under the control of a summing valve 45, the body 46 of which is connected to link 26 by a pin and slot connection 48.
  • the inner rotor 53 of the valve 45 is oscillated by a command actuator 50 having a piston 52 mechanically connected to the rotor 53.
  • This connection is indicated in FIG. 1 as a link 54, but may be any other suitable connection such as will be later described in connection with FIGS. 3, 4, 5 and 6.
  • the supply conduits 56 and 58 between command valve 40 and command actuator 50 may include suitable adjustable restrictions 60 and 62 with associated check valves for the purpose of regulating the speed of motion of the piston 52.
  • the command actuator 50 also operates a synchromotor 64 for generating a feedback signal derived from the position of the piston 52.
  • the pump displacement regulating mechanism utilizes a servomotor comprising small area piston 66 subjected to constant pilot control pressure through branch line 68 and a large area piston 70 under the control of three-way directional valve 72 which is supplied with pressure through branch line 74.
  • Pump 38 also supplies charging fluid to the pump 34 through priority valve 76 and branch line 78 leading to the usual checkvalves 80 connected to the main power lines 28 and 30.
  • a control pressure relief valve 82 limits the charging pressure while a shuttle valve 84 and higher pressure relief valve 86 serve as secondary protection for the main power lines 28 and 30. Primary protection for them is provided by checkvalves 88 and pilot operated relief valve 90-92.
  • helm device 94 which may be an automatic pilot or a manual helm switching device, may be connected by lines 96-98 to control the command valve 40.
  • One line supplies a port rudder signal of uniform magnitude while the other supplies a similar starboard rudder signal. It will be understood that although a single line is illustrated, these each represent the usual two wire connection.
  • the command actuator position as received at the synchromotor 64 is transmitted as an electrical signal through lines 100 to the bridge, where it may serve to supply either an autopilot or a rudder position repeater in the usual manner.
  • the body 46 of the summing valve 45 has a tubular stem 102 rotatable in a bore 104 of the body 50 and has secured to it at its outer end an arm 106 (see FIG. 7).
  • the outer end of arm 106 is connected by link 108 to the pin 48 and link 26 coming from the rotor of the main rudder motor.
  • the summing valve rotor 53 is formed at the lower end of an oscillating shaft 110 mounted in the bore of the sleeve 102 and in a bore 112 in the body 50.
  • the summing valve 45 provides a pair of variable resistances, one for each of two bleed circuits 114 and 116 (see FIG. 2) which form part of a hydraulic bridge controlling the valve 72.
  • the rotor 53 is formed with a pair of arcuate grooves 118 leading to the lower end of the stem 110 in FIG. 3, and connected to reservoir through the central passage 120.
  • Each of the variable resistances is comprised of a pair of dimetrically opposite ports 122 and 124 respectively, these ports being connected together by drilled passages 126 and 128 respectively.
  • the bleed circuits 114 and 116 connect to the ports 122 and 124 respectivelyby flexible hoses.
  • the shaft 110 is connected to the rotor 130 of synchromotor 64, the body of which is mounted by a bracket 132 to the body 50.
  • the stem 110 which constitutes the rotor 53 of the summing valve is arranged to be connected for oscillatory movement by a radial arm 54 in FIG. 3 which extends through a bore in a trunnion pin 134 carried by the piston 52.
  • longitudinal movement of the piston 52 (FIG. 4) will produce oscillatory movement of the stem 110.
  • the resistance at ports 122 and 124 may be varied equally and oppositely as the stem 110 moves away from its center position in one direction or the other. This reciprocally changes the resistance in the bleed circuits 114 and 116 and because of the hydraulic bridge circuit charateristics, causes the valve 72 to shift to one direction or the other and energize or deenergize the large area servomotor 70.
  • a similar pair of variable resistances are contained in a response valve 136 (FIG. 2) which receive pilot control fluid through a branch 138 and distributes it to the two bleed circuits 114 and 116 at rates which depend upon the position of the stroke regulating mechanism of the pump 34.
  • the hydraulic bridge control circuit may be similar to that illustrated in the copending application of Robert H. Breeden, Ser. No. 182,677, now U.S. Pat. No. 3,758,235 filed Sept. 22, 1971 for Power Transmission.
  • the maximum throw of the rudder motor 10 may be regulated by limiting the stroke of the command actuator piston 52.
  • the piston 52 may be provided with pins 140 on its ends which engage with adjustable poppet valves 142 mounted in the ends of the body 50. These poppet valves are in the fluid inlet and outlet passages 144 and, when seated, serve to block further ingress of fluid to their respective ends of the cylinder. By raising or lowering the body of the poppet valve 142, it is possible to vary the point at which the pin 140 allows the poppet to seat and thus limits the stroke of the piston 52.
  • a ships rudder control system comprising a hydraulic rudder motor and a reversible variable displacement pump for shifting the motor, means for controlling the pump displacement including a servomotor and a hydraulic bridge having a pair of bleed circuits carrying a continuous small flow of pilot control fluid, command means for varying the resistance in a first portion of the bleed circuits, response means for varying the resistance in a second portion of the bleed circuits as the pump displacement changes, said command means including a first member movable at command and a sec- 0nd member movable in follow-up motion responsive to shifting of the rudder motor.
  • a system as defined in claim 1 which includes a hy-' draulic actuator for the command means and a closed loop servo system connected to drive the actuator in response to helm input.
  • a system as defined in claim 3 including a position responsive electrical feed-back device driven by the actuator and electrically connected to the helm.
  • a system as defined in claim 4 having a common source of pilot control fluid for the pump servomotor,

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Servomotors (AREA)
US00218183A 1972-01-17 1972-01-17 Power transmission Expired - Lifetime US3799096A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US00218183A US3799096A (en) 1972-01-17 1972-01-17 Power transmission
DE2301622A DE2301622C3 (de) 1972-01-17 1973-01-13 Elektrohydraulische Schiffsrudersteuereinrichtung
GB216373A GB1411002A (en) 1972-01-17 1973-01-16 Ships rudder control systems
JP732873A JPS5320638B2 (US07922777-20110412-C00004.png) 1972-01-17 1973-01-16
FR7301396A FR2168375B3 (US07922777-20110412-C00004.png) 1972-01-17 1973-01-16
SE7300556A SE382031B (sv) 1972-01-17 1973-01-16 Manoveranleggning for fartygsroder

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00218183A US3799096A (en) 1972-01-17 1972-01-17 Power transmission

Publications (1)

Publication Number Publication Date
US3799096A true US3799096A (en) 1974-03-26

Family

ID=22814076

Family Applications (1)

Application Number Title Priority Date Filing Date
US00218183A Expired - Lifetime US3799096A (en) 1972-01-17 1972-01-17 Power transmission

Country Status (6)

Country Link
US (1) US3799096A (US07922777-20110412-C00004.png)
JP (1) JPS5320638B2 (US07922777-20110412-C00004.png)
DE (1) DE2301622C3 (US07922777-20110412-C00004.png)
FR (1) FR2168375B3 (US07922777-20110412-C00004.png)
GB (1) GB1411002A (US07922777-20110412-C00004.png)
SE (1) SE382031B (US07922777-20110412-C00004.png)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4140075A (en) * 1977-07-08 1979-02-20 Paul-Munroe Hydraulies, Inc. Steering control system for ships
US4408555A (en) * 1981-06-16 1983-10-11 Aung U Soe Ships steering gear
US4933617A (en) * 1987-08-12 1990-06-12 Hoerbiger Hydraulik Gmbh Servo steering system for motor boats
ES2119596A1 (es) * 1994-07-27 1998-10-01 Univ Cantabria Sistema de gobierno automatico de accionamiento variable de timones de buques.
EP1826118A1 (en) * 2006-02-24 2007-08-29 AVIO S.p.A. Autopilot assembly for a naval unit

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5774703U (US07922777-20110412-C00004.png) * 1980-10-27 1982-05-08
JPS60140411U (ja) * 1984-02-29 1985-09-17 井上　八郎 靴用滑り止め
JPS60153208U (ja) * 1984-03-21 1985-10-12 井上　八郎 靴用滑り止め

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1854226A (en) * 1929-05-17 1932-04-19 Waterbury Tool Co Hydraulic steering gear for ships
US2175800A (en) * 1937-01-14 1939-10-10 Sperry Gyroscope Co Inc Electrohydraulic steering gear
US2667746A (en) * 1953-06-12 1954-02-02 American Eng Co Ltd Steering apparatus
US2988306A (en) * 1955-10-17 1961-06-13 Honeywell Regulator Co Aircraft surface control
US3527186A (en) * 1968-06-14 1970-09-08 Propulsion Systems Inc Variable rate electrohydraulic actuator systems,particularly for ship's steering and/or propeller pitch control

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1854226A (en) * 1929-05-17 1932-04-19 Waterbury Tool Co Hydraulic steering gear for ships
US2175800A (en) * 1937-01-14 1939-10-10 Sperry Gyroscope Co Inc Electrohydraulic steering gear
US2667746A (en) * 1953-06-12 1954-02-02 American Eng Co Ltd Steering apparatus
US2988306A (en) * 1955-10-17 1961-06-13 Honeywell Regulator Co Aircraft surface control
US3527186A (en) * 1968-06-14 1970-09-08 Propulsion Systems Inc Variable rate electrohydraulic actuator systems,particularly for ship's steering and/or propeller pitch control

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4140075A (en) * 1977-07-08 1979-02-20 Paul-Munroe Hydraulies, Inc. Steering control system for ships
US4408555A (en) * 1981-06-16 1983-10-11 Aung U Soe Ships steering gear
US4933617A (en) * 1987-08-12 1990-06-12 Hoerbiger Hydraulik Gmbh Servo steering system for motor boats
ES2119596A1 (es) * 1994-07-27 1998-10-01 Univ Cantabria Sistema de gobierno automatico de accionamiento variable de timones de buques.
EP1826118A1 (en) * 2006-02-24 2007-08-29 AVIO S.p.A. Autopilot assembly for a naval unit

Also Published As

Publication number Publication date
JPS4880960A (US07922777-20110412-C00004.png) 1973-10-30
FR2168375B3 (US07922777-20110412-C00004.png) 1976-01-16
SE382031B (sv) 1976-01-12
DE2301622A1 (de) 1973-07-26
DE2301622C3 (de) 1975-07-03
FR2168375A1 (US07922777-20110412-C00004.png) 1973-08-31
GB1411002A (en) 1975-10-22
JPS5320638B2 (US07922777-20110412-C00004.png) 1978-06-28
DE2301622B2 (de) 1974-11-21

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Legal Events

Date Code Title Description
AS Assignment

Owner name: SPERRY CORPORATION

Free format text: CHANGE OF NAME;ASSIGNOR:SPERRY RAND CORPORATION;REEL/FRAME:003794/0122

Effective date: 19790824

AS Assignment

Owner name: VICKERS, INCORPORATED TROY, MI A DE CORP

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST. EFFECTIVE NOVEMBER 2, 1983;ASSIGNOR:SPERRY CORPORATION A DE CORP.;REEL/FRAME:004337/0889

Effective date: 19831102

Owner name: VICKERS, INCORPORATED,MICHIGAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SPERRY CORPORATION A DE CORP.;REEL/FRAME:004337/0889

Effective date: 19831102