CN111828418B - Full-rotating rudder propeller hydraulic system - Google Patents

Full-rotating rudder propeller hydraulic system Download PDF

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Publication number
CN111828418B
CN111828418B CN202010474433.6A CN202010474433A CN111828418B CN 111828418 B CN111828418 B CN 111828418B CN 202010474433 A CN202010474433 A CN 202010474433A CN 111828418 B CN111828418 B CN 111828418B
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oil
valve
port
communicated
way reversing
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CN111828418A (en
Inventor
张三喜
汤波
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Wuhan Marine Machinery Plant Co Ltd
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Wuhan Marine Machinery Plant Co Ltd
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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/14—Fluid pressure control

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The utility model provides a rudder propeller hydraulic system that turns round belongs to rudder propeller control field that turns round entirely. The full-rotation rudder propeller hydraulic system comprises an oil tank, a hydraulic pump set, a rudder propeller control assembly and a rotation control assembly, wherein the rudder propeller control assembly comprises a two-position three-way reversing valve and a hydraulic clutch, and the rotation control assembly comprises a first three-position four-way reversing valve, a first motor and a second motor. The utility model provides a rudder propeller hydraulic system that turns around entirely not only can realize the control to hydraulic clutch through one set of hydraulic system, can also realize the control to the motor to effective reduce cost.

Description

Full-rotating rudder propeller hydraulic system
Technical Field
The disclosure belongs to the field of control of a full-turning rudder propeller, and particularly relates to a hydraulic system of a full-turning rudder propeller.
Background
The full-rotation rudder propeller is an underwater propulsion device which can provide thrust in a 360-degree range, can enable a ship to have good operation performance and dynamic positioning performance, and is widely applied to various ocean ships and ocean engineering platforms.
In the related art, a full-turning rudder propeller hydraulic system includes a rudder propeller control hydraulic system and a turning control hydraulic system that are independent of each other. For a steering oar control hydraulic system, hydraulic oil in an oil tank of a full-rotation steering oar body provides power for the work of a hydraulic clutch, so that the connection between the steering oar and a diesel engine is controlled. For a rotary control hydraulic system, hydraulic oil in a rotary oil tank provides pressure oil for a motor, so that the full rotary direction of a steering oar is controlled.
However, the two sets of hydraulic systems each require an oil tank, a plurality of control valves, pipelines, and the like, which results in high cost.
Disclosure of Invention
The embodiment of the disclosure provides a full-rotation rudder propeller hydraulic system, which can not only realize the control of a hydraulic clutch but also realize the control of a motor through one set of hydraulic system, thereby effectively reducing the cost.
The technical scheme is as follows:
the embodiment of the disclosure provides a full-turning rudder propeller hydraulic system, which comprises an oil tank, a hydraulic pump set, a rudder propeller control assembly and a turning control assembly;
an oil inlet of the hydraulic pump set is communicated with an oil outlet of the oil tank;
the steering oar control assembly comprises a two-position three-way reversing valve and a hydraulic clutch, an oil inlet of the two-position three-way reversing valve is communicated with an oil outlet of the hydraulic pump set, an oil return port of the two-position three-way reversing valve is communicated with an oil return port of the oil tank, and a working oil port of the two-position three-way reversing valve is communicated with the hydraulic clutch;
the rotary control assembly comprises a first three-position four-way reversing valve, a first motor and a second motor, an oil inlet of the first three-position four-way reversing valve is communicated with an oil outlet of the hydraulic pump set, an oil return port of the first three-position four-way reversing valve is communicated with an oil return port of the oil tank, a first working oil port of the first three-position four-way reversing valve is communicated with a first oil port of the first motor and a first oil port of the second motor respectively, and a second working oil port of the first three-position four-way reversing valve is communicated with a second oil port of the first motor and a second oil port of the second motor respectively.
Optionally, the full-rotation rudder propeller hydraulic system further comprises a pressure control assembly, the pressure control assembly comprises a first overflow valve, a second overflow valve, a two-position two-way reversing valve and a first shuttle valve, an oil inlet and a first control oil port of the first overflow valve are both communicated with an oil outlet of the hydraulic pump set, an oil inlet and a first control oil port of the second overflow valve are both communicated with an oil return port of the two-position two-way reversing valve, an oil inlet of the two-position two-way reversing valve is communicated with an oil outlet of the hydraulic pump set, an oil outlet of the first overflow valve and an oil outlet of the second overflow valve are both communicated with an oil return port of the oil tank, a first working oil port of the first shuttle valve is communicated with a first working oil port of the first three-position four-way reversing valve, a second working oil port of the first shuttle valve is communicated with a second working oil port of the first three-position four-way reversing valve, and the oil outlet of the first shuttle valve is respectively communicated with the second control oil port of the first overflow valve and the second control oil port of the second overflow valve.
Optionally, the pressure control assembly further comprises a third overflow valve, an oil inlet and a control oil port of the third overflow valve are both communicated with an oil outlet of the hydraulic pump group, and an oil outlet of the third overflow valve is communicated with an oil return port of the oil tank.
Optionally, the rudder propeller control assembly includes the relief pressure valve, the oil inlet of relief pressure valve with the oil-out intercommunication of hydraulic pump package, the oil-out and the control hydraulic fluid port of relief pressure valve all with the oil inlet intercommunication of two tee bend switching-over valves, the draining port of relief pressure valve with the oil return opening intercommunication of oil tank.
Optionally, the rotation control assembly further includes a one-way throttle valve, a second shuttle valve, and a brake cylinder for controlling braking of the first motor, an oil inlet of the one-way throttle valve is communicated with an oil outlet of the second shuttle valve, an oil outlet of the one-way throttle valve is communicated with a rod cavity of the brake cylinder, a first oil port of the second shuttle valve is communicated with a first working oil port of the first three-position four-way reversing valve, and a second oil port of the second shuttle valve is communicated with a second working oil port of the first three-position four-way reversing valve.
Optionally, the hydraulic pump group includes a first gear pump and a second gear pump, the full-turn rudder paddle hydraulic system further includes a second three-position four-way reversing valve, an oil inlet of the first gear pump, an oil inlet of the second gear pump all communicate with an oil outlet of the oil tank, an oil outlet of the first gear pump communicates with an oil inlet of the first three-position four-way reversing valve, an oil outlet of the second gear pump communicates with an oil inlet of the second three-position four-way reversing valve, an oil return port of the second three-position four-way reversing valve communicates with an oil return port of the oil tank, a first working oil port of the second three-position four-way reversing valve communicates with a first working oil port of the first three-position four-way reversing valve, and a second working oil port of the second three-position four-way reversing valve communicates with a second working oil port of the first three-position four-way reversing valve.
Optionally, the rotation control assembly further includes a first balance valve, the first balance valve includes a first valve body and a first check valve, the oil inlet of the first valve body and the oil inlet of the first check valve are all communicated with the first working oil port of the first three-position four-way reversing valve, the oil outlet of the first valve body, the first control oil port of the first valve body and the oil outlet of the first check valve are all communicated with the first oil port of the first motor and the first oil port of the second motor, and the second control oil port of the first valve body is communicated with the second working oil port of the first three-position four-way reversing valve.
Optionally, the rotation control assembly further includes a second balance valve, the second balance valve includes a second valve body and a second check valve, an oil inlet of the second valve body and an oil inlet of the second check valve are both communicated with a second working oil port of the first three-position four-way reversing valve, an oil outlet of the second valve body, a first control oil port of the second valve body and an oil outlet of the second check valve are all communicated with a second oil port of the first motor and a second oil port of the second motor, and a second control oil port of the second valve body is communicated with a first working oil port of the first three-position four-way reversing valve.
Optionally, the rotation control assembly further includes a fourth overflow valve and a fifth overflow valve, an oil inlet and a control oil port of the fourth overflow valve are both communicated with the first working oil port of the first three-position four-way reversing valve, an oil outlet of the fourth overflow valve is communicated with the second working oil port of the first three-position four-way reversing valve, an oil inlet and a control oil port of the fifth overflow valve are both communicated with the second working oil port of the first three-position four-way reversing valve, and an oil outlet of the fourth overflow valve is communicated with the first working oil port of the first three-position four-way reversing valve.
Optionally, the rotation control assembly further comprises a two-position four-way reversing valve, an oil inlet of the two-position four-way reversing valve is communicated with a first working oil port of the first three-position four-way reversing valve, an oil return port of the two-position four-way reversing valve is communicated with a second working oil port of the first three-position four-way reversing valve, the first working oil port of the two-position four-way reversing valve is communicated with a first oil port of the first motor and a first oil port of the second motor respectively, and the second working oil port of the two-position four-way reversing valve is communicated with a second oil port of the first motor and a second oil port of the second motor respectively.
The technical scheme provided by the embodiment of the disclosure has the following beneficial effects:
in the full-rotation rudder propeller hydraulic system provided by the embodiment of the disclosure, for the rudder propeller control assembly, when the valve core of the two-position three-way reversing valve is arranged at the right position, hydraulic oil pumped out by the hydraulic pump unit flows into the hydraulic clutch through the oil inlet and the working oil port of the two-position three-way reversing valve, so that the hydraulic clutch is attached to a diesel engine, and the connection and the drainage of the rudder propeller are realized. When the valve core of the two-position three-way reversing valve is arranged at the left position, hydraulic oil flows into the oil tank through the hydraulic clutch, the working oil port and the oil return port of the two-position three-way reversing valve, so that the hydraulic clutch is separated from the diesel engine, and the displacement of the steering oar is realized.
For the rotary control assembly, when the valve core of the first three-position four-way reversing valve is arranged at the right position, hydraulic oil flows into the first oil port of the first motor and the first oil port of the second motor simultaneously from the oil outlet of the hydraulic pump set, the oil inlet of the first three-position four-way reversing valve and the first working oil port of the first three-position four-way reversing valve in sequence. The hydraulic oil flowing out of the second oil port of the first motor and the second oil port of the second motor sequentially passes through the second working oil port and the oil return port of the first three-position four-way reversing valve, and then flows back to the oil tank, so that the forward rotation of the first motor and the second motor is completed, and the forward rotation of the steering oar can be realized. When the valve core of the first three-position four-way reversing valve is arranged at the left position, hydraulic oil flows into the second oil port of the first motor and the second oil port of the second motor simultaneously from the oil outlet of the hydraulic pump set, the oil inlet of the first three-position four-way reversing valve and the second working oil port of the first three-position four-way reversing valve in sequence. The hydraulic oil flowing out of the first oil port of the first motor and the first oil port of the second motor sequentially passes through the first working oil port and the oil return port of the first three-position four-way reversing valve, and then flows back to the oil tank, so that the first motor and the second motor are reversed, and the reverse rotation of the steering oar can be realized. When the valve core of the first three-position four-way reversing valve is placed in the middle position, the first motor and the second motor are in a standby state.
That is to say, through the rudder propeller hydraulic system that turns round that this disclosed embodiment provided, not only can realize the control to hydraulic clutch through one set of hydraulic system, can also realize the control to the motor, still make the quantity of oil tank, valve member and pipeline all reduce in addition to effective reduce cost.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present disclosure, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present disclosure, and it is obvious for those skilled in the art to obtain other drawings based on the drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a rudder propeller hydraulic system according to an embodiment of the present disclosure;
FIG. 2 is an enlarged view of a portion of area A of FIG. 1;
fig. 3 is a partially enlarged view of the region B in fig. 1.
The symbols in the drawings represent the following meanings:
1. an oil tank; 2. a hydraulic pump unit; 21. a first gear pump; 22. a second gear pump; 3. a rudder paddle control assembly; 31. a two-position three-way reversing valve; 32. a hydraulic clutch; 33. a pressure reducing valve; 4. a swing control assembly; 41. a first three-position four-way reversing valve; 42. a first motor; 43. a second motor; 44. a first counter-balance valve; 441. a first valve body; 442. a first check valve; 45. a second balancing valve; 451. a second valve body; 452. a second one-way valve; 46. a fourth overflow valve; 47. a fifth overflow valve; 48. a two-position four-way reversing valve; 5. a pressure control assembly; 51. a first overflow valve; 52. a second overflow valve; 53. a two-position two-way reversing valve; 54. a first shuttle valve; 55. a third overflow valve; 6. a one-way throttle valve; 61. a check valve body; 62. a throttle body; 7. a second shuttle valve; 8. a brake cylinder; 9. a second three-position four-way reversing valve; 10. a sixth relief valve; 11. a one-way valve; 12. maintaining the valve; 100. a diesel engine.
Detailed Description
To make the objects, technical solutions and advantages of the present disclosure more apparent, embodiments of the present disclosure will be described in detail with reference to the accompanying drawings.
Fig. 1 is a schematic structural diagram of a rudder propeller hydraulic system according to an embodiment of the present disclosure, and as shown in fig. 1, the rudder propeller hydraulic system includes an oil tank 1, a hydraulic pump unit 2, a rudder propeller control assembly 3, and a steering control assembly 4.
An oil inlet of the hydraulic pump set 2 is communicated with an oil outlet of the oil tank 1.
Fig. 2 is a partial enlarged view of an area a in fig. 1, and as shown in fig. 2, the rudder propeller control assembly 3 includes a two-position three-way directional valve 31 and a hydraulic clutch 32, an oil inlet p of the two-position three-way directional valve 31 is communicated with an oil outlet of the hydraulic pump group 2, an oil return port t of the two-position three-way directional valve 31 is communicated with an oil return port of the oil tank 1, and a working oil port a of the two-position three-way directional valve 31 is communicated with the hydraulic clutch 32.
The rotation control assembly 4 comprises a first three-position four-way reversing valve 41, a first motor 42 and a second motor 43, an oil inlet p of the first three-position four-way reversing valve 41 is communicated with an oil outlet of the hydraulic pump unit 2, an oil return port t of the first three-position four-way reversing valve 41 is communicated with an oil return port of the oil tank 1, a first working oil port a of the first three-position four-way reversing valve 41 is respectively communicated with a first oil port a of the first motor 42 and a first oil port a of the second motor 43, and a second working oil port b of the first three-position four-way reversing valve 41 is respectively communicated with a second oil port b of the first motor 42 and a second oil port b of the second motor 43.
In the full-rotation rudder propeller hydraulic system provided by the embodiment of the present disclosure, for the rudder propeller control assembly 3, when the spool of the two-position three-way directional valve 31 is disposed at the right position, hydraulic oil pumped out by the hydraulic pump unit 2 flows into the hydraulic clutch 32 through the oil inlet p and the working oil port a of the two-position three-way directional valve 31, so that the hydraulic clutch 32 is attached to the diesel engine 100, thereby realizing the row and row of the rudder propeller. When the valve core of the two-position three-way directional valve 31 is arranged at the left position, hydraulic oil flows into the oil tank 1 through the hydraulic clutch 32, the working oil port a and the oil return port t of the two-position three-way directional valve 31, so that the hydraulic clutch 32 is separated from the diesel engine 100, and the displacement of the steering oar is realized.
For the rotation control assembly 4, when the valve core of the first three-position four-way reversing valve 41 is positioned at the right position, the hydraulic oil flows through the oil outlet of the hydraulic pump unit 2, the oil inlet p of the first three-position four-way reversing valve 41, the first working oil port a of the first three-position four-way reversing valve 41, and simultaneously flows into the first oil port a of the first motor 42 and the first oil port a of the second motor 43. The hydraulic oil flowing out from the second oil port b of the first motor 42 and the second oil port b of the second motor 43 sequentially passes through the second working oil port b and the oil return port t of the first three-position four-way reversing valve 41, and then flows back to the oil tank 1, so that the forward rotation of the first motor 42 and the second motor 43 is completed, and the forward rotation of the rudder propeller can be realized. When the valve core of the first three-position four-way selector valve 41 is positioned at the left position, the hydraulic oil flows from the oil outlet of the hydraulic pump unit 2, the oil inlet p of the first three-position four-way selector valve 41, the second working oil port b of the first three-position four-way selector valve 41, and simultaneously flows into the second oil port b of the first motor 42 and the second oil port b of the second motor 43. The hydraulic oil flowing out from the first oil port a of the first motor 42 and the first oil port a of the second motor 43 sequentially passes through the first working oil port a and the oil return port t of the first three-position four-way directional valve 41, and then flows back to the oil tank 1, so that the reverse rotation of the first motor 42 and the second motor 43 is completed, and the reverse rotation of the rudder propeller can be realized. When the spool of the first three-position four-way selector valve 41 is placed in the neutral position, the first motor 42 and the second motor 43 are in a standby state.
That is to say, through the rudder propeller hydraulic system that turns round that this disclosed embodiment provided, not only can realize the control to hydraulic clutch through one set of hydraulic system, can also realize the control to the motor, still make the quantity of oil tank, valve member and pipeline all reduce in addition to effective reduce cost.
With continued reference to fig. 2, the hydraulic system of the full-slewing rudder propeller further includes a pressure control assembly 5, the pressure control assembly 5 includes a first overflow valve 51, a second overflow valve 52, a two-position two-way reversing valve 53 and a first shuttle valve 54, an oil inlet a and a first control oil port c of the first overflow valve 51 are both communicated with an oil outlet of the hydraulic pump unit 2, an oil inlet a and a first control oil port c of the second overflow valve 52 are both communicated with an oil return port t of the two-position two-way reversing valve 53, an oil inlet of the two-position two-way reversing valve 53 is communicated with an oil outlet of the hydraulic pump unit 2, an oil outlet b of the first overflow valve 51 and an oil outlet b of the second overflow valve 52 are both communicated with an oil return port of the oil tank 1, a first working oil port a of the first shuttle valve 54 is communicated with a first working oil port a of the first three-position four-way reversing valve 41, a second working oil port b of the first shuttle valve 54 is communicated with a second working oil port b of the first three-position four-way reversing valve 41, an oil outlet c of the first shuttle valve 54 is respectively communicated with a second control port d of the first overflow valve 51 and a second control port d of the second overflow valve 52.
In the above embodiment, the opening pressures of the first and second relief valves 51 and 52 can be controlled by the first shuttle valve 54, so that energy saving and temperature reduction are effectively achieved when the first and second motors 42 and 43 are in the standby state, and the hydraulic clutch 32 can be ensured to work normally when the first and second motors 42 and 43 are in the standby state.
Illustratively, when the spool of the first three-position, four-way selector valve 41 is placed in the neutral position, the first motor 42 and the second motor 43 are in a standby state. At this time, if the spool of the two-position two-way selector valve 53 is positioned at the upper position, the opening pressure P of the first relief valve 51 is increased 1 Is less than the opening pressure P of the second relief valve 52 2 Therefore, the second relief valve 52 is open, and the hydraulic system pressure (P) at this time 1 ) Low, energy saving and temperature reduction can be achieved, and the system pressure is not enough to enable the hydraulic clutch 32 to be started. At this time, if the spool of the two-position two-way selector valve 53 is in the low position, the second relief valve 52 is in the open state, so that the first relief valve 51 is open, and the hydraulic system pressure (P) is at this time 2 ) Higher, system pressure may maintain activation of hydraulic clutch 32.
When the spool of the first three-position four-way selector valve 41 is in the left or right position, the hydraulic system pressure is P 3 (P 3 ＞P 2 ＞P 1 ) Because the first shuttle valve 54 guides the hydraulic oil into the second control port d of the first overflow valve 51 or the second control port d of the second overflow valve 52, both the first overflow valve 51 and the second overflow valve 52 are turned off, and thus both the first overflow valve 51 and the second overflow valve 52 are disabled, and the circulation of the hydraulic oil is not affected by the first overflow valve 51 or the second overflow valve 52. While the hydraulic system is adjusted to P when the first motor 42 or the second motor 43 is on standby 1 Or P 2 Therefore, the hydraulic system can effectively save energy and reduce temperature.
Optionally, the pressure control assembly 5 further includes a third overflow valve 55, an oil inlet a and a control oil port c of the third overflow valve 55 are both communicated with an oil outlet of the hydraulic pump group 2, and an oil outlet b of the third overflow valve 55 is communicated with an oil return port of the oil tank 1.
In the above embodiment, the third relief valve 55 can control the hydraulic pressure in the hydraulic system, preventing the pressure in the hydraulic system from being excessive.
Optionally, the rudder propeller control assembly 3 includes a pressure reducing valve 33, an oil inlet a of the pressure reducing valve 33 is communicated with an oil outlet of the hydraulic pump unit 2, an oil outlet b and a control oil port c of the pressure reducing valve 33 are both communicated with an oil inlet p of the two-position three-way reversing valve 31, and an oil drainage port d of the pressure reducing valve 33 is communicated with an oil return port of the oil tank 1.
In the above manner, the pressure reducing valve 33 can effectively control the pressure entering the hydraulic clutch 32, and avoid damage to the hydraulic clutch 32 caused by too much pressure.
Fig. 3 is a partial enlarged view of a region B in fig. 1, and as shown in fig. 3, the rotation control assembly 4 further includes a first balance valve 44, the first balance valve 44 includes a first valve body 441 and a first check valve 442, an oil inlet a of the first valve body 441 and an oil inlet a of the first check valve 442 are both communicated with a first working oil port a of the first three-position four-way reversing valve 41, an oil outlet B of the first valve body 441, a first control oil port c of the first valve body 441 and an oil outlet B of the first check valve 442 are both communicated with a first oil port a of the first motor 42 and a first oil port a of the second motor 43, and a second control oil port d of the first valve body 441 is communicated with a second working oil port B of the first three-position four-way reversing valve 41.
In the above embodiment, the first balancing valve 44 may prevent the hydraulic oil from flowing back to the first working port a of the first three-position four-way selector valve 41 through the first motor 42 or the second motor 43 and dropping too quickly, thereby preventing the first motor 42 or the second motor 43 from stalling.
Optionally, the rotation control assembly 4 further includes a second balance valve 45, the second balance valve 45 includes a second valve body 451 and a second check valve 452, an oil inlet a of the second valve body 451 and an oil inlet a of the second check valve 452 are both communicated with the second working oil port b of the first three-position four-way reversing valve 41, an oil outlet b of the second valve body 451, a first control oil port c of the second valve body 451, and an oil outlet b of the second check valve 452 are both communicated with the second oil port b of the first motor 42 and the second oil port b of the second motor 43, and a second control oil port d of the second valve body 451 is communicated with the first working oil port a of the first three-position four-way reversing valve 41.
In the above embodiment, the second balancing valve 45 prevents the pressure drop of the hydraulic oil from flowing back to the second working port b of the first three-position four-way selector valve 41 through the first motor 42 or the second motor 43 from being too fast, thereby preventing the first motor 42 or the second motor 43 from stalling.
Illustratively, the oil drain port e of the first valve body 441 is communicated with the oil inlet a, so that the hydraulic oil leaked by the first valve body 441 can be returned to the pipeline. The oil drain port e of the second valve body 451 communicates with the oil inlet a so that the hydraulic oil leaking from the second valve body 451 can be returned to the pipeline.
Optionally, the rotation control assembly 4 further includes a fourth overflow valve 46 and a fifth overflow valve 47, an oil inlet a and a control oil port c of the fourth overflow valve 46 are both communicated with the first working oil port a of the first three-position four-way reversing valve 41, an oil outlet b of the fourth overflow valve 46 is communicated with the second working oil port b of the first three-position four-way reversing valve 41, an oil inlet a and a control oil port c of the fifth overflow valve 47 are both communicated with the second working oil port b of the first three-position four-way reversing valve 41, and an oil outlet b of the fourth overflow valve 46 is communicated with the first working oil port a of the first three-position four-way reversing valve 41.
In the above embodiment, the fourth relief valve 46 and the fifth relief valve 47 can effectively prevent the hydraulic oil pressure entering the first motor 42 or the second motor 43 from being excessively large.
Illustratively, the swing control assembly 4 further includes a service valve 12, and the service valve 12 is located between the first working oil port a and the second working oil port b of the first three-position four-way selector valve 41.
In this way, servicing of the first and second motors 42, 43 is facilitated.
Optionally, the rotation control assembly 4 further includes a one-way throttle valve 6, a second shuttle valve 7, and a brake cylinder 8 for controlling braking of the first motor 42, an oil inlet a of the one-way throttle valve 6 is communicated with an oil outlet c of the second shuttle valve 7, an oil outlet b of the one-way throttle valve 6 is communicated with a rod cavity of the brake cylinder 8, a first oil port a of the second shuttle valve 7 is communicated with a first working oil port a of the first three-position four-way reversing valve 41, and a second oil port b of the second shuttle valve 7 is communicated with a second working oil port b of the first three-position four-way reversing valve 41.
In the above embodiment, the brake of the first motor 42 can be effectively controlled by the brake cylinder 8, so as to control the brake of the steering oar.
Illustratively, the check throttle 6 includes a check valve body 61 and a throttle body 62.
Illustratively, when the first motor 42 and the second motor 43 are operated, the second shuttle valve 7 selects the hydraulic oil of which the pressure is large in the first oil port a and the second oil port b to flow into the rod chamber of the brake cylinder 8 through the check valve body 61, so that the piston rod of the brake cylinder 8 is retracted, thereby releasing the brake. When the first motor 42 and the second motor 43 do not work, no pressure oil exists in the second shuttle valve 7, and hydraulic oil flows through the rod cavity of the brake oil cylinder 8, the throttle valve body 62, the second shuttle valve 7 and the first three-position four-way reversing valve 41 in sequence to flow back, so that the piston rod extends out, and the braking effect is achieved.
Optionally, the rotation control assembly 4 further includes a two-position four-way reversing valve 48, an oil inlet p of the two-position four-way reversing valve 48 is communicated with a first working oil port a of the first three-position four-way reversing valve 41, an oil return port t of the two-position four-way reversing valve 48 is communicated with a second working oil port b of the first three-position four-way reversing valve 41, a first working oil port a of the two-position four-way reversing valve 48 is respectively communicated with a first oil port a of the first motor 42 and a first oil port a of the second motor 43, and a second working oil port b of the two-position four-way reversing valve 48 is respectively communicated with a second oil port b of the second motor 43 and a second oil port b of the first motor 42.
For example, the two-position, four-way reversing valve 48 may control the starting and standby of the first motor 42 and the second motor 43.
Referring to fig. 1 again, the hydraulic pump group 2 includes a first gear pump 21 and a second gear pump 22, the full-slewing rudder propeller hydraulic system further includes a second three-position four-way directional valve 9, an oil inlet of the first gear pump 21 and an oil inlet of the second gear pump 22 are both communicated with an oil outlet of the oil tank 1, an oil outlet of the first gear pump 21 is communicated with an oil inlet of the first three-position four-way directional valve 41, an oil outlet of the second gear pump 22 is communicated with an oil inlet p of the second three-position four-way directional valve 9, an oil return port t of the second three-position four-way directional valve 9 is communicated with an oil return port of the oil tank 1, a first working oil port a of the second three-position four-way directional valve 9 is communicated with a first working oil port a of the first three-position four-way directional valve 41, and a second working oil port b of the second three-position four-way directional valve 9 is communicated with a second working oil port b of the first three-position four-way directional valve 41.
In the above embodiment, the first gear pump 21 can control the first motor 42 and the second motor 43 to rotate at a low speed. The second gear pump 22 can control the first motor 42 and the second motor 43 to rotate at a high speed. The first gear pump 21 and the second gear pump 22 work simultaneously to control the first motor 42 and the second motor 43 to rotate at high speed.
It should be noted that the first gear pump 21 and the second gear pump 22 are dual gear pumps, that is, the first gear pump 21 and the second gear pump 22 are both driven by the same diesel engine 100, so that the number of driving devices is reduced, and cost saving is facilitated.
In this embodiment, a sixth relief valve 10 is provided between the oil inlet p and the oil return port t of the second three-position four-way reversing valve 9, and the function of the sixth relief valve is the same as that of the third relief valve 55, which is not described again.
Illustratively, check valves 11 are arranged between an oil outlet of the first gear pump 21 and the first three-position four-way reversing valve 41 and between the second gear pump 22 and the second three-position four-way reversing valve 9, and all the check valves play a role in preventing hydraulic oil from flowing back.
In this embodiment, the two-position three-way selector valve 31, the first three-position four-way selector valve 41, the two-position four-way selector valve 48, the two-position two-way selector valve 53, and the second three-position four-way selector valve 9 may be solenoid valves, so that the labor can be effectively saved.
The working principle of the hydraulic system of the rudder propeller provided by the present disclosure is briefly explained as follows:
for the steering oar control assembly 3, when the valve core of the two-position three-way reversing valve 31 is arranged at the right position, the hydraulic oil pumped out by the hydraulic pump unit 2 flows into the hydraulic clutch 32 through the oil inlet p and the working oil port a of the two-position three-way reversing valve 31, so that the hydraulic clutch 32 is attached to the diesel engine 100, and the connection and the drainage of the steering oar are realized. When the valve core of the two-position three-way directional valve 31 is arranged at the left position, hydraulic oil flows into the oil tank 1 through the hydraulic clutch 32, the working oil port a and the oil return port t of the two-position three-way directional valve 31, so that the hydraulic clutch 32 is separated from the diesel engine 100, and the displacement of the steering oar is realized.
For the rotation control assembly 4, when the valve core of the first three-position four-way reversing valve 41 is positioned at the right position, the hydraulic oil flows from the oil outlet of the hydraulic pump set 2, the oil inlet p of the first three-position four-way reversing valve 41, the first working oil port a of the first three-position four-way reversing valve 41, and simultaneously flows into the first oil port a of the first motor 42 and the first oil port a of the second motor 43. The hydraulic oil flowing out from the second oil port b of the first motor 42 and the second oil port b of the second motor 43 sequentially passes through the second working oil port b and the oil return port t of the first three-position four-way reversing valve 41, and then flows back to the oil tank 1, so that the forward rotation of the first motor 42 and the second motor 43 is completed, and the forward rotation of the rudder propeller can be realized. When the valve core of the first three-position four-way selector valve 41 is positioned at the left position, the hydraulic oil flows from the oil outlet of the hydraulic pump unit 2, the oil inlet p of the first three-position four-way selector valve 41, the second working oil port b of the first three-position four-way selector valve 41, and simultaneously flows into the second oil port b of the first motor 42 and the second oil port b of the second motor 43. The hydraulic oil flowing out from the first oil port a of the first motor 42 and the first oil port a of the second motor 43 sequentially passes through the first working oil port a and the oil return port t of the first three-position four-way directional valve 41, and then flows back to the oil tank 1, so that the reverse rotation of the first motor 42 and the second motor 43 is completed, and the reverse rotation of the rudder propeller can be realized. When the spool of the first three-position four-way selector valve 41 is placed in the neutral position, the first motor 42 and the second motor 43 are in a standby state.
The above description is intended to be exemplary only and not to limit the present disclosure, and any modification, equivalent replacement, or improvement made without departing from the spirit and scope of the present disclosure is to be considered as the same as the present disclosure.

Claims (10)

1. The hydraulic system of the full-turning rudder propeller is characterized by comprising an oil tank (1), a hydraulic pump set (2), a rudder propeller control assembly (3) and a turning control assembly (4);
an oil inlet of the hydraulic pump set (2) is communicated with an oil outlet of the oil tank (1);
the steering oar control assembly (3) comprises a two-position three-way reversing valve (31) and a hydraulic clutch (32), an oil inlet of the two-position three-way reversing valve (31) is communicated with an oil outlet of the hydraulic pump set (2), an oil return port of the two-position three-way reversing valve (31) is communicated with an oil return port of the oil tank (1), and a working oil port of the two-position three-way reversing valve (31) is communicated with the hydraulic clutch (32);
the rotary control assembly (4) comprises a first three-position four-way reversing valve (41), a first motor (42) and a second motor (43), an oil inlet of the first three-position four-way reversing valve (41) is communicated with an oil outlet of the hydraulic pump set (2), an oil return port of the first three-position four-way reversing valve (41) is communicated with an oil return port of the oil tank (1), a first working oil port of the first three-position four-way reversing valve (41) is communicated with a first oil port of the first motor (42) and a first oil port of the second motor (43) respectively, and a second working oil port of the first three-position four-way reversing valve (41) is communicated with a second oil port of the first motor (42) and a second oil port of the second motor (43) respectively.
2. The rudder propeller hydraulic system according to claim 1, further comprising a pressure control assembly (5), wherein the pressure control assembly (5) comprises a first overflow valve (51), a second overflow valve (52), a two-position two-way reversing valve (53) and a first shuttle valve (54), an oil inlet and a first control oil port of the first overflow valve (51) are both communicated with an oil outlet of the hydraulic pump set (2), an oil inlet and a first control oil port of the second overflow valve (52) are both communicated with an oil return port of the two-position two-way reversing valve (53), an oil inlet of the two-position two-way reversing valve (53) is communicated with an oil outlet of the hydraulic pump set (2), an oil outlet of the first overflow valve (51) and an oil outlet of the second overflow valve (52) are both communicated with an oil return port of the oil tank (1), a first working oil port of the first shuttle valve (54) is communicated with a first working oil port of the first three-position four-way reversing valve (41), a second working oil port of the first shuttle valve (54) is communicated with a second working oil port of the first three-position four-way reversing valve (41), and an oil outlet of the first shuttle valve (54) is respectively communicated with a second control oil port of the first overflow valve (51) and a second control oil port of the second overflow valve (52).
3. The rudder propeller hydraulic system according to claim 2, wherein the pressure control assembly (5) further comprises a third overflow valve (55), an oil inlet and a control oil port of the third overflow valve (55) are both communicated with an oil outlet of the hydraulic pump unit (2), and an oil outlet of the third overflow valve (55) is communicated with an oil return port of the oil tank (1).
4. The rudder propeller hydraulic system according to claim 1, wherein the rudder propeller control assembly (3) includes a pressure reducing valve (33), an oil inlet of the pressure reducing valve (33) is communicated with an oil outlet of the hydraulic pump unit (2), the oil outlet and a control oil port of the pressure reducing valve (33) are communicated with an oil inlet of the two-position three-way reversing valve (31), and an oil drain port of the pressure reducing valve (33) is communicated with an oil return port of the oil tank (1).
5. The hydraulic system of the full-turn rudder propeller according to claim 1, wherein the turn control assembly (4) further comprises a one-way throttle valve (6), a second shuttle valve (7) and a brake cylinder (8) for controlling the brake of the first motor (42), an oil inlet of the one-way throttle valve (6) is communicated with an oil outlet of the second shuttle valve (7), an oil outlet of the one-way throttle valve (6) is communicated with a rod cavity of the brake cylinder (8), a first oil port of the second shuttle valve (7) is communicated with a first working oil port of the first three-position four-way reversing valve (41), and a second oil port of the second shuttle valve (7) is communicated with a second working oil port of the first three-position four-way reversing valve (41).
6. The full-rotary rudder propeller hydraulic system according to claim 1, wherein the hydraulic pump group (2) comprises a first gear pump (21) and a second gear pump (22), the full-rotary rudder propeller hydraulic system further comprises a second three-position four-way reversing valve (9), an oil inlet of the first gear pump (21) and an oil inlet of the second gear pump (22) are both communicated with an oil outlet of the oil tank (1), an oil outlet of the first gear pump (21) is communicated with an oil inlet of the first three-position four-way reversing valve (41), an oil outlet of the second gear pump (22) is communicated with an oil inlet of the second three-position four-way reversing valve (9), an oil return port of the second three-position four-way reversing valve (9) is communicated with an oil return port of the oil tank (1), a first working oil port of the second three-position four-way reversing valve (9) is communicated with a first working oil port of the first three-position four-way reversing valve (41), and a second working oil port of the second three-position four-way reversing valve (9) is communicated with a second working oil port of the first three-position four-way reversing valve (41).
7. The hydraulic system of the full-turn rudder propeller according to claim 1, wherein the turn control assembly (4) further comprises a first balance valve (44), the first balance valve (44) comprises a first valve body (441) and a first check valve (442), an oil inlet of the first valve body (441) and an oil inlet of the first check valve (442) are both communicated with a first working oil port of the first three-position four-way reversing valve (41), an oil outlet of the first valve body (441), a first control oil port of the first valve body (441), and an oil outlet of the first check valve (442) are both communicated with a first oil port of the first motor (42) and a first oil port of the second motor (43), and a second control oil port of the first valve body (441) is communicated with a second working oil port of the first three-position four-way reversing valve (41).
8. The hydraulic system of the full-turn rudder propeller according to claim 1, wherein the turn control assembly (4) further comprises a second balance valve (45), the second balance valve (45) comprises a second valve body (451) and a second check valve (452), an oil inlet of the second valve body (451) and an oil inlet of the second check valve (452) are both communicated with a second working oil port of the first three-position four-way reversing valve (41), an oil outlet of the second valve body (451), a first control oil port of the second valve body (451), and an oil outlet of the second check valve (452) are both communicated with a second oil port of the first motor (42) and a second oil port of the second motor (43), and a second control oil port of the second valve body (451) is communicated with a first working oil port of the first three-position four-way reversing valve (41).
9. The all-turn rudder paddle hydraulic system according to any one of claims 1 to 8, wherein the turn control assembly (4) further comprises a fourth overflow valve (46) and a fifth overflow valve (47), an oil inlet and a control oil port of the fourth overflow valve (46) are both communicated with a first working oil port of the first three-position four-way reversing valve (41), an oil outlet of the fourth overflow valve (46) is communicated with a second working oil port of the first three-position four-way reversing valve (41), an oil inlet and a control oil port of the fifth overflow valve (47) are both communicated with a second working oil port of the first three-position four-way reversing valve (41), and an oil outlet of the fourth overflow valve (46) is communicated with a first working oil port of the first three-position four-way reversing valve (41).
10. The hydraulic system of the full-rotary rudder propeller according to any one of claims 1 to 8, wherein the rotary control assembly (4) further comprises a two-position four-way reversing valve (48), an oil inlet of the two-position four-way reversing valve (48) is communicated with a first working oil port of the first three-position four-way reversing valve (41), an oil return port of the two-position four-way reversing valve (48) is communicated with a second working oil port of the first three-position four-way reversing valve (41), a first working oil port of the two-position four-way reversing valve (48) is respectively communicated with a first oil port of the first motor (42) and a first oil port of the second motor (43), and a second working oil port of the two-position four-way reversing valve (48) is respectively communicated with a second oil port of the first motor (42) and a second oil port of the second motor (43).
CN202010474433.6A 2020-05-29 2020-05-29 Full-rotating rudder propeller hydraulic system Active CN111828418B (en)

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Publication number Priority date Publication date Assignee Title
CN2066843U (en) * 1989-12-01 1990-12-05 张文华 Multi-function composite hydraulic steering engine
CN109139579A (en) * 2018-08-29 2019-01-04 武汉船用机械有限责任公司 A kind of hydraulic control system and its control method of full-rotating rudder paddle
CN109809311A (en) * 2019-01-31 2019-05-28 武汉船用机械有限责任公司 The Hydraulic slewing system and crane of crane
CN109812513A (en) * 2019-01-31 2019-05-28 武汉船用机械有限责任公司 The hydraulic control system of hydraulic clutch

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8840438B2 (en) * 2010-12-22 2014-09-23 Brp Us Inc. Hydraulic system for a watercraft

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2066843U (en) * 1989-12-01 1990-12-05 张文华 Multi-function composite hydraulic steering engine
CN109139579A (en) * 2018-08-29 2019-01-04 武汉船用机械有限责任公司 A kind of hydraulic control system and its control method of full-rotating rudder paddle
CN109809311A (en) * 2019-01-31 2019-05-28 武汉船用机械有限责任公司 The Hydraulic slewing system and crane of crane
CN109812513A (en) * 2019-01-31 2019-05-28 武汉船用机械有限责任公司 The hydraulic control system of hydraulic clutch

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