CN110143271B - Pump-controlled hydraulic steering engine - Google Patents
Pump-controlled hydraulic steering engine Download PDFInfo
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- CN110143271B CN110143271B CN201910246952.4A CN201910246952A CN110143271B CN 110143271 B CN110143271 B CN 110143271B CN 201910246952 A CN201910246952 A CN 201910246952A CN 110143271 B CN110143271 B CN 110143271B
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- 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
- B63H25/24—Transmitting of movement of initiating means to steering engine by electrical means
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- 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
- B63H25/26—Steering engines
- B63H25/28—Steering engines of fluid type
- B63H25/30—Steering engines of fluid type hydraulic
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- Chemical & Material Sciences (AREA)
- Engineering & Computer Science (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a pump-controlled hydraulic steering engine, and belongs to the field of steering engines. The pump accuse hydraulic steering wheel includes: the engine base, the rudder pushing mechanism, the control unit, the hydraulic station and the first oil supplementing unit, wherein the rudder pushing mechanism comprises a first plunger oil cylinder and a second plunger oil cylinder, the utility model provides a hydraulic pressure station, the plunger, tiller and rudderstock, the both ends of plunger are located first plunger hydro-cylinder and second plunger hydro-cylinder respectively, the one end and the plunger of rudderstock are connected, and the one end of rudderstock is located between first plunger hydro-cylinder and the second plunger hydro-cylinder, the other end of rudderstock is located to the rudderstock, the rudderstock is used for driving the rudder blade rotatory, hydraulic pressure station includes first motor, first hydraulic pump and drive valves, first motor is used for driving first hydraulic pump to rotate, first hydraulic pump includes first pump body, locate first working oil port and second working oil port on the first pump body, first working oil port passes through the no plunger chamber intercommunication of drive valves and first plunger hydro-cylinder, the no plunger chamber intercommunication of second working oil port through drive valves and second plunger hydro-cylinder.
Description
Technical Field
The invention relates to the field of steering engines, in particular to a pump-controlled hydraulic steering engine.
Background
The device which takes hydraulic oil as a working medium and can steer the ship and keep the steering position is called as a hydraulic steering engine. The hydraulic steering engine has the working principle that the pump outputs high-pressure oil to drive the rudder blade to rotate under the drive of the motor. According to different steering control modes of the steering engine, the hydraulic steering engine can be divided into a valve control hydraulic steering engine and a pump control hydraulic steering engine. The difference between the two is that the valve-controlled hydraulic steering engine controls the direction of high-pressure oil output by the pump through a reversing valve, so that the reversing operation of a rudder blade is realized; the pump-controlled hydraulic steering engine adjusts the direction of high-pressure oil output by the small pump by controlling the small pump to rotate forwards and backwards through the motor, so that the steering operation of the rudder blade is realized.
Traditional pump accuse hydraulic steering wheel generally adopts the structure of the formula of pulling the prarson-shifting fork, mainly includes tiller, plunger, hydro-cylinder, variable pump and pump control device, and its theory of operation includes: a steering angle instruction is sent by a steering table, and a swash plate in the variable displacement pump is inclined through a pump control device, so that pressure oil is discharged; the pressure oil pushes a plunger in the oil cylinder to move in a translation way, and the plunger drives the tiller to rotate; the rotation is transmitted to the rudder stock and the rudder blade by the rudder stock, and the steering of the ship is realized.
In the process of implementing the invention, the inventor finds that the prior art has at least the following problems: one end of the tiller is connected with the plunger through the plunger pin and the roller, the other end of the tiller is suspended, the tiller is fixed at the other end of the tiller, and the stability of the tiller is poor when the tiller rotates due to the fact that the other end bears the dual gravity of the tiller and the tiller.
Disclosure of Invention
The embodiment of the invention provides a pump-controlled hydraulic steering engine which can ensure the rotation stability of a tiller. The technical scheme is as follows:
the invention provides a pump-controlled hydraulic steering engine, which comprises: the hydraulic station comprises a first motor, a first hydraulic pump and a driving valve group, the first motor is used for driving the first hydraulic pump to rotate, the first hydraulic pump comprises a first pump body, a first working oil port and a second working oil port which are arranged on the first pump body, the first working oil port is communicated with a plunger-free cavity of the first plunger oil cylinder through the driving valve group, the second hydraulic fluid port passes through the drive valves with the no plunger chamber intercommunication of second plunger hydro-cylinder, first oil supplementing unit includes piston hydro-cylinder, second motor, second hydraulic pump, pressure adjustment valves and oil tank, piston hydro-cylinder is fixed in the frame, be equipped with the piston rod in the piston hydro-cylinder, the one end of piston rod stretches out outside the piston hydro-cylinder and with the other end of tiller is connected, the second motor is used for the drive the second hydraulic pump rotates, the second hydraulic pump includes the second pump body, locates third working fluid port and fourth working fluid port on the second pump body, the third working fluid port passes through the pressure adjustment valves with the no rod chamber intercommunication of piston hydro-cylinder, the fourth working fluid port with the oil tank intercommunication.
Optionally, the pressure regulating valve pack comprises: a first pressure reducing overflow valve and a second pressure reducing overflow valve,
the first pressure reducing overflow valve comprises a first valve body, a first oil inlet, a first oil outlet and a first oil drainage port which are arranged on the first valve body, the second pressure reducing overflow valve comprises a second valve body, a second oil inlet, a second oil outlet and a second oil drainage port which are arranged on the second valve body,
the first oil inlet of the first pressure reduction overflow valve is communicated with the third working oil port of the second hydraulic pump, the second oil inlet of the second pressure reduction overflow valve and the rodless cavity of the piston oil cylinder respectively, the second oil inlet of the second pressure reduction overflow valve is communicated with the third working oil port of the second hydraulic pump and the rodless cavity of the piston oil cylinder respectively, and the first oil outlet, the first oil drainage port of the first pressure reduction overflow valve, the second oil outlet of the second pressure reduction overflow valve and the second oil drainage port of the second pressure reduction overflow valve are communicated with the oil tank respectively.
Optionally, the pressure regulating valve group further comprises a reversing valve,
and a first oil inlet of the first pressure reduction overflow valve and a second oil inlet of the second pressure reduction overflow valve are respectively communicated with the rodless cavity of the piston oil cylinder through the reversing valve.
Optionally, a filter is disposed between the first oil outlet of the first pressure reduction overflow valve and the oil tank, and between the second oil outlet of the second pressure reduction overflow valve and the oil tank.
Optionally, the pump-controlled hydraulic steering engine further comprises a second oil supplementing unit,
the second oil supplementing unit comprises a first oil supplementing valve and a second oil supplementing valve, oil inlets of the first oil supplementing valve and the second oil supplementing valve are communicated with the oil tank, an oil outlet of the first oil supplementing valve is communicated with a first working oil port of the first hydraulic pump and a plunger-free cavity of the first plunger oil cylinder respectively, and an oil outlet of the second oil supplementing valve is communicated with a second working oil port of the first hydraulic pump and a plunger-free cavity of the second plunger oil cylinder respectively.
Optionally, the driving valve set includes an unloading solenoid valve, an oil outlet of the unloading solenoid valve is communicated with the oil tank, and an oil inlet of the unloading solenoid valve is respectively communicated with the first working oil port of the first hydraulic pump, the plunger-free cavity of the first plunger cylinder and the plunger-free cavity of the second plunger cylinder.
Optionally, the driving valve set includes a two-way safety valve, a first oil port of the two-way safety valve is respectively communicated with a first working oil port of the first hydraulic pump and a plunger-free cavity of the first plunger cylinder, and a second oil port of the two-way safety valve is respectively communicated with a second working oil port of the first hydraulic pump and a plunger-free cavity of the second plunger cylinder.
Optionally, the first motor is a variable frequency motor.
Optionally, the first hydraulic pump is a fixed displacement pump.
Optionally, the control unit is configured to,
receiving a steering indication, wherein the steering indication comprises a target steering angle;
and adjusting the rotating speed and the rotating direction of the first motor based on the target rudder angle.
The technical scheme provided by the embodiment of the invention has the following beneficial effects: the first hydraulic pump is communicated with a plunger-free cavity of the first plunger cylinder through the driving valve group, and the second hydraulic pump is communicated with a plunger-free cavity of the second plunger cylinder through the driving valve group, so that the first hydraulic pump rotates under the driving of the first motor, high-pressure oil is conveyed to the first plunger cylinder and the second plunger cylinder through the driving valve group and pushes the plungers to translate, the plungers drive the rudderstock to rotate, the rudderstock transmits the rotation to the rudderstock, and the rudderstock drives the rudder blade to rotate, so that the steering of the ship is realized; a piston rod is arranged in the piston oil cylinder, one end of the piston rod extends out of the piston oil cylinder and is connected with the other end of the tiller, so that when the plunger moves and drives the piston rod to move, the rodless cavity space of the piston oil cylinder is small, redundant oil in the first oil supplementing unit flows back to the oil tank through the pressure regulating valve group; when the plunger moves and drives the piston rod to move, so that the space of a rodless cavity of the piston oil cylinder is enlarged, oil is supplied to the piston oil cylinder through the second motor and the second hydraulic pump through the pressure regulating valve group; under the two conditions, the piston rod overcomes the pressure movement of pressure oil, so the piston rod reacts on the plunger, the moving speed of the plunger tends to a certain range, the moving stability of the plunger is kept, the balance effect of the tiller is achieved, and the rotating stability of the tiller is ensured.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a pump-controlled hydraulic steering engine according to an embodiment of the present invention.
In the drawing, 1 engine base, 2 steering mechanism, 21 first plunger cylinder, 22 second plunger cylinder, 23 plunger, 24 tiller, 25 tiller, 3 hydraulic station, 31 first motor, 32 first hydraulic pump, 33 driving valve group, 33a unloading electromagnetic valve, 33b two-way safety valve, 4 first oil supplementing unit, 41 piston cylinder, 42 second motor, 43 second hydraulic pump, 44 pressure regulating valve group, 45 oil tank, 44a first pressure reducing overflow valve, 44b second pressure reducing overflow valve, 44c reversing valve, 44d filter, 5 second oil supplementing unit, 51 first oil supplementing valve, 52 second oil supplementing valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
In traditional pump accuse hydraulic steering wheel, asynchronous machine is generally selected for use to the motor, and the variable pump is generally selected for use to the hydraulic pump to adopt the volume speed governing mode to adjust the pump speed, this mode has following shortcoming:
firstly, the self-suction capability of the oil pump is reduced when the oil pump runs at low speed, and cavitation, noise, flow pulse and the like are formed to cause unstable operation of the steering engine.
Secondly, the inertia of the asynchronous motor greatly influences the rapidity of command response.
Thirdly, the speed regulation range is limited and is limited by the swing angle amplitude of the swash plate of the variable displacement pump.
Fourthly, in the process of sucking and discharging the small-flow hydraulic oil, the variable pump is still in a high-speed running state, the noise is large, the efficiency of the motor changes along with the change of the load, and the system efficiency is low.
Fig. 1 shows a pump-controlled hydraulic steering engine according to an embodiment of the present invention. Referring to fig. 1, the pump-controlled hydraulic steering engine includes: a machine base 1, a rudder pushing mechanism 2, a control unit (not shown), a hydraulic station 3 and a first oil supplementing unit 4.
The rudder pushing mechanism 2 comprises a first plunger cylinder 21, a second plunger cylinder 22, a plunger 23, a tiller 24 and a tiller; the two ends of the plunger 23 are respectively positioned in the first plunger cylinder 21 and the second plunger cylinder 22, one end of the tiller 24 is connected with the plunger 23, one end of the tiller 24 is positioned between the first plunger cylinder 21 and the second plunger cylinder 22, the tiller is arranged at the other end of the tiller 24, and the tiller is used for driving the rudder blade to rotate.
The hydraulic station 3 comprises a first electric motor 31, a first hydraulic pump 32 and a drive valve group 33; the first hydraulic pump 32 includes a first pump body, and a first working oil port and a second working oil port which are provided on the first pump body, the first working oil port is communicated with the plunger-free cavity of the first plunger cylinder 21 through the driving valve group 33, and the second working oil port is communicated with the plunger-free cavity of the second plunger cylinder 22 through the driving valve group 33.
The first oil supplementing unit 4 comprises a piston oil cylinder 41, a second motor 42, a second hydraulic pump 43, a pressure regulating valve group 44 and an oil tank 45; the piston cylinder 41 is fixed on the base 1, a piston rod is arranged in the piston cylinder 41, one end of the piston rod extends out of the piston cylinder 41 and is connected with the other end of the tiller 24, the second motor 42 is used for driving the second hydraulic pump 43 to rotate, the second hydraulic pump 43 comprises a second pump body, a third working oil port and a fourth working oil port, the third working oil port is arranged on the second pump body and is communicated with a rodless cavity of the piston cylinder 41 through a pressure regulating valve group 44, and the fourth working oil port is communicated with an oil tank 45.
Specifically, one end of the tiller 24 is connected to the plunger 23 through a plunger pin and a roller (not shown), which convert the movement of the plunger 23 into a rotational movement of the roller, thereby rotating the tiller 24.
The first working oil port of the first hydraulic pump 32 is communicated with the plunger-free cavity of the first plunger cylinder 21 through the driving valve group 33, and the second working oil port is communicated with the plunger-free cavity of the second plunger cylinder 22 through the driving valve group 33, so that the first hydraulic pump 32 rotates under the driving of the first motor 31, high-pressure oil is conveyed to the first plunger cylinder 21 and the second plunger cylinder 22 through the driving valve group 33 and pushes the plunger 23 to translate, the plunger 23 drives the tiller 24 to rotate, the tiller 24 transmits the rotation to the tiller, and the rudder blade is driven to rotate by the tiller, so that the steering of the ship is realized; a piston rod is arranged in the piston cylinder 41, one end of the piston rod extends out of the piston cylinder 41 and is connected with the other end of the tiller 24, so that when the plunger 23 moves and drives the piston rod to move, and the space of a rodless cavity of the piston cylinder 41 is small, redundant oil in the first oil supplementing unit 4 flows back to the oil tank 45 through the pressure regulating valve group 44; when the plunger 23 moves and drives the piston rod to move so that the rodless cavity space of the piston cylinder 41 becomes larger, oil is supplemented to the piston cylinder 41 through the second motor 42 and the second hydraulic pump 43 through the pressure regulating valve group 44; in both cases, the piston rod is moved against the pressure of the pressure oil, so the piston rod will act against the plunger 23, the moving speed of the plunger 23 tends to a certain range, the moving stability of the plunger 23 is maintained, the balancing effect of the tiller is achieved, and the rotating stability of the tiller 24 is ensured.
Illustratively, the first motor 31 is a variable frequency motor. Firstly, the variable frequency motor can be started and stopped frequently, current impact cannot be generated, the steering engine can be stopped under the condition of no operation, and the safety of the steering engine is improved. Secondly, the inertia of the variable frequency motor is smaller than that of the asynchronous motor, and the variable frequency motor can respond to the instruction of the control unit more quickly.
Illustratively, the first hydraulic pump 32 is a fixed displacement pump. Compared with a variable pump, the constant delivery pump has high reliability and strong adaptability to the system environment, and the noise of the constant delivery pump is smaller.
In the hydraulic station 3, for example, see fig. 1, the drive valve block 33 comprises an unloading solenoid valve 33 a. An oil outlet of the unloading electromagnetic valve 33a is communicated with the oil tank 45, and an oil inlet of the unloading electromagnetic valve 33a is respectively communicated with a first working oil port of the first hydraulic pump 32, a plunger-free cavity of the first plunger cylinder 21 and a plunger-free cavity of the second plunger cylinder 22. Among them, the unloading solenoid valve 33a is used to open and close under the instruction of the control unit. When the unloading electromagnetic valve 33a is opened, the oil inlet and the oil outlet of the unloading electromagnetic valve 33a are disconnected, and at this time, the hydraulic oil in the oil path flows into the oil tank 45 through the unloading electromagnetic valve 33 a; when the unloading solenoid valve 33a is closed, the oil inlet and the oil outlet of the unloading solenoid valve 33a are communicated, and hydraulic oil in the oil path cannot flow into the oil tank 45 through the unloading solenoid valve 33 a.
The working process of the hydraulic station 3 comprises: the control unit receives a steering indication, wherein the steering indication comprises a target steering angle; the control unit adjusts the rotation speed and the rotation direction of the first motor 31 based on the target rudder angle. Specifically, the control unit adjusts the rotation speed and the rotation direction of the first motor 31 based on the target rudder angle and the current rudder angle. The first motor 31 drives the first hydraulic pump 32 to operate, the control unit synchronously controls the unloading electromagnetic valve 33a to be opened, after the unloading electromagnetic valve 33a is opened, an oil inlet and an oil outlet of the unloading electromagnetic valve 33a are cut off, namely, an unloading loop between the hydraulic station 3 and the oil tank 45 is cut off, oil discharged by the first hydraulic pump 32 controls the rotation direction of a rudder blade through the movement direction of a rudder stock through the movement of the plunger 23, and further controls the movement direction of a ship. When the control unit detects that the current rudder angle reaches the target rudder angle, the control unit reduces the rotating speed of the first motor 31, and further drives the rotating speed of the first hydraulic pump 32 to decrease, so that the system oil amount is reduced, and the plunger 23 stops swinging.
Optionally, referring to fig. 1, the drive valve block 33 further includes a two-way relief valve 33 b. The first port of the two-way relief valve 33b is communicated with the first working port of the first hydraulic pump 32 and the non-plunger chamber of the first plunger cylinder 21, respectively, and the second port of the two-way relief valve 33b is communicated with the second working port of the first hydraulic pump 32 and the non-plunger chamber of the second plunger cylinder 22, respectively. The two-way relief valve 33 ensures safety of oil pressure during oil passage into and out of the first plunger cylinder 21 and the second plunger cylinder 22 and during reversing. Specifically, after the air-hydraulic steering engine starts to be started, the first oil port and the second oil port of the two-way safety valve 33b are in an unconnected state. Assuming that the first working oil port of the first hydraulic pump 32 discharges hydraulic oil, at this time, when the pressure of the first oil port of the two-way safety valve 33b reaches the target pressure, the second oil port of the two-way safety valve 33b is communicated with the first oil port to discharge hydraulic oil of the target flow rate, so as to reduce the hydraulic oil pressure in the oil path; assuming that the second working port of the first hydraulic pump 32 discharges the hydraulic oil, when the pressure of the second port of the two-way relief valve 33b reaches the target pressure, the second port of the two-way relief valve 33b communicates with the first port to discharge the hydraulic oil at the target flow rate, thereby reducing the hydraulic oil pressure in the oil path.
The pressure regulating valve set 44 is used for controlling the pressure value of the piston cylinder 41, so as to maintain the stability of the rotation of the tiller 24 and prevent cavitation or over-high pressure. In the first oil compensation unit 4, as shown in fig. 1, the pressure regulating valve group 44 illustratively includes: a first pressure reducing relief and relief valve 44a and a second pressure reducing relief and relief valve 44 b. The first pressure-reducing overflow valve 44a comprises a first valve body, a first oil inlet, a first oil outlet and a first oil drainage port which are arranged on the first valve body, and the second pressure-reducing overflow valve 44b comprises a second valve body, a second oil inlet, a second oil outlet and a second oil drainage port which are arranged on the second valve body. The first oil inlet of the first pressure reducing overflow valve 44a is respectively communicated with the third working oil port of the second hydraulic pump 43, the second oil inlet of the second pressure reducing overflow valve 44b and the rodless cavity of the piston cylinder 41. A second oil inlet of the second pressure reducing and overflowing valve 44b is respectively communicated with a third working oil port of the second hydraulic pump 43 and a rodless cavity of the piston cylinder 41. The first oil outlet of the first pressure-reducing overflow valve 44a, the first oil drainage port, the second oil outlet of the second pressure-reducing overflow valve 44b and the second oil drainage port are respectively communicated with an oil tank 45. The first pressure-reducing relief valve 44a and the second pressure-reducing relief valve 44b are both hydraulic pressure control valves, and play a role in constant pressure relief, system unloading and safety protection in hydraulic equipment. Such as: in a fixed displacement pump (second hydraulic pump 43) throttling condition system, the fixed displacement pump provides a constant flow rate that decreases the flow demand as the system pressure increases. And the redundant flow overflows back to the oil tank through the overflow valve at the moment, so that the system pressure is ensured. Specifically, taking the first pressure reducing and overflowing valve 44a as an example, the first oil inlet of the first pressure reducing and overflowing valve 44a is at an indefinite oil inlet pressure, the first oil outlet is at a constant oil outlet pressure (within a target range), and the first oil drainage port is used for discharging oil after the oil inlet pressure is adjusted.
When the plunger 23 moves and drives the piston rod to move, so that the rodless cavity space of the piston cylinder 41 is small, redundant oil in the first oil supplementing unit 4 flows back to the oil tank 45 through the pressure regulating valve group 44; when the plunger 23 moves and drives the piston rod to move so that the rodless cavity space of the piston cylinder 41 becomes larger, oil is supplemented to the piston cylinder 41 through the second motor 42 and the second hydraulic pump 43 through the pressure regulating valve group 44; in both cases, since the piston rod is moved against the pressure of the pressure oil, the piston rod will act against the plunger 23, so that the moving speed of the plunger 23 tends to a certain range, and the stability of the movement of the plunger 23 is maintained.
Specifically, the first pressure-reducing relief valve 44a and the second pressure-reducing relief valve 44b are both direct-acting pressure-reducing valves having relief valve functions.
Illustratively, referring to fig. 1, the pressure regulating valve set 44 also includes a reversing valve 44 c. The first oil inlet of the first pressure reducing relief valve 44a and the second oil inlet of the second pressure reducing relief valve 44b are respectively communicated with the rodless cavity of the piston cylinder 41 through a selector valve 44 c. The reversing valve 44c changes the oil path in the valve by changing different positions, so that the oil paths at the outlet are different, thereby playing a reversing role.
It should be noted that an oil passage (one end of which is not connected in fig. 1) is further connected to the oil passage between the direction changing valve 44c and the rodless chamber of the piston cylinder 41, and the oil passage may communicate with an oil tank 45 for adjusting the pressure between the direction changing valve 44c and the rodless chamber of the piston cylinder 41.
For example, referring to fig. 1, a filter 44d is provided between the first outlet of the first pressure-reducing relief valve 44a and the oil tank 45, and between the second outlet of the second pressure-reducing relief valve 44b and the oil tank 45. The filter 44d filters the oil discharged to the oil tank 45 to remove impurities.
The steering engine mainly drives the steering engine to move by hydraulic oil, the sealing element arranged inside the steering engine plays a role in preventing hydraulic oil leakage, but the leakage of the hydraulic oil can be caused due to the aging of the sealing element and the aging of the valve piece, and the poor quality of the processing surfaces of the plunger 23, the valve group and other workpieces. The leakage of hydraulic oil can cause the phenomena of crawling, vibration, noise and the like when the steering engine works. In order to solve this problem, the pump-controlled hydraulic steering engine further includes a second oil supply unit 5, for example. The second oil replenishment unit 5 includes a first oil replenishment valve 51 and a second oil replenishment valve 52. Oil inlets of the first oil replenishing valve 51 and the second oil replenishing valve 52 are communicated with the oil tank 45, an oil outlet of the first oil replenishing valve 51 is communicated with a first working oil port of the first hydraulic pump 32 and a plunger-free cavity of the first plunger cylinder 21 respectively, and an oil outlet of the second oil replenishing valve 52 is communicated with a second working oil port of the first hydraulic pump 32 and a plunger-free cavity of the second plunger cylinder 22 respectively.
The first oil replenishing valve 51 and the second oil replenishing valve 52 replenish oil to the first hydraulic pump 32, so that the self-priming capacity of the first hydraulic pump 32 can be prevented from being reduced when the first hydraulic pump is operated at a low speed, and unstable operation of the steering engine caused by cavitation, noise, flow pulse and the like can be avoided. In addition, variable displacement pumps are noisy, in large part due to fluid noise. The fluid noise of a hydraulic pump is mainly caused by the periodic variation of the pressure and flow rate of the pump and cavitation. Thus, cavitation, noise and flow pulse are avoided, and fluid noise is reduced, and further hydraulic pump noise is reduced.
Illustratively, the control unit is configured to control the rotation speed of the first motor 31 to 0 when the rudder angle reaches the target rudder angle. Thereby saving energy loss.
In this embodiment, the hydraulic station 3 is a closed hydraulic station 3, and the closed system is more energy-saving than the open system because the main oil path of the closed system is not provided with other valves such as the reversing valve 44c except for the hydraulic lock, thereby reducing pressure loss. The closed hydraulic station 3 combines the variable frequency motor technology, compared with the traditional steering engine of a valve control system and a pump control system, the variable frequency steering engine is simple in system and sensitive in action, the reversible variable frequency motor and the hydraulic bidirectional oil pump are matched to adjust the flow in the system, the rotating speed of the steering engine is controlled, stepless speed regulation of the discharge capacity is realized, the plunger 23 in the oil cylinder is ensured to be stably pushed, and the operation stability and efficiency of the steering engine are ensured.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (7)
1. The utility model provides a pump accuse hydraulic steering wheel which characterized in that, pump accuse hydraulic steering wheel includes: the rudder propelling mechanism comprises a base (1), a rudder propelling mechanism (2), a control unit, a hydraulic station (3) and a first oil supplementing unit (4), wherein the rudder propelling mechanism (2) comprises a first plunger oil cylinder (21), a second plunger oil cylinder (22), a plunger (23), a tiller (24) and a tiller (25), two ends of the plunger (23) are respectively located in the first plunger oil cylinder (21) and the second plunger oil cylinder (22), one end of the tiller (24) is connected with the plunger (23), one end of the tiller (24) is located between the first plunger oil cylinder (21) and the second plunger oil cylinder (22), the tiller (25) is arranged at the other end of the tiller (24), the tiller (25) is used for driving a tiller blade to rotate, the hydraulic station (3) comprises a first motor (31), a first hydraulic pump (32) and a driving valve group (33), the first motor (31) is used for driving the first hydraulic pump (32) to rotate, the first hydraulic pump (32) comprises a first pump body, a first working oil port and a second working oil port which are arranged on the first pump body, the first working oil port is communicated with a plunger (23) -free cavity of the first plunger oil cylinder (21) through the driving valve group (33), the second working oil port is communicated with a plunger-free cavity of the second plunger oil cylinder (22) through the driving valve group (33), the first oil supplementing unit (4) comprises a piston oil cylinder (41), a second motor (42), a second hydraulic pump (43), a pressure adjusting valve group (44) and an oil tank (45), the piston oil cylinder (41) is fixed on the machine base (1), a piston rod is arranged in the piston oil cylinder (41), one end of the piston rod extends out of the piston oil cylinder (41) and is connected with the other end of the tiller (24), the second motor (42) is used for driving the second hydraulic pump (43) to rotate, the second hydraulic pump (43) comprises a second pump body, and a third working oil port and a fourth working oil port which are arranged on the second pump body, the third working oil port is communicated with a rodless cavity of the piston oil cylinder (41) through the pressure regulating valve group (44), and the fourth working oil port is communicated with the oil tank (45);
the second hydraulic pump (43) is a fixed displacement pump,
the pressure regulating valve group (44) comprises: a first pressure reducing relief valve (44a) and a second pressure reducing relief valve (44b),
the first pressure reducing overflow valve (44a) comprises a first valve body, a first oil inlet, a first oil outlet and a first oil drainage port which are arranged on the first valve body, the second pressure reducing overflow valve (44b) comprises a second valve body, a second oil inlet, a second oil outlet and a second oil drainage port which are arranged on the second valve body,
a first oil inlet of the first pressure reduction overflow valve (44a) is respectively communicated with a third working oil port of the second hydraulic pump (43), a second oil inlet of the second pressure reduction overflow valve (44b) and a rodless cavity of the piston oil cylinder (41), a second oil inlet of the second pressure reduction overflow valve (44b) is respectively communicated with a third working oil port of the second hydraulic pump (43) and a rodless cavity of the piston oil cylinder (41), a first oil outlet of the first pressure reduction overflow valve (44a), a first oil drainage port, a second oil outlet of the second pressure reduction overflow valve (44b) and a second oil drainage port are respectively communicated with the oil tank (45),
the drive valve group (33) comprises an unloading electromagnetic valve (33a), an oil outlet of the unloading electromagnetic valve (33a) is communicated with the oil tank (45), an oil inlet of the unloading electromagnetic valve (33a) is respectively communicated with a first working oil port of the first hydraulic pump (32), a plunger-free cavity of the first plunger oil cylinder (21) and a plunger-free cavity of the second plunger oil cylinder (22), the unloading electromagnetic valve (33a) is used for opening and closing under the instruction of a control unit, when the unloading electromagnetic valve (33a) is opened, an oil inlet and an oil outlet of the unloading electromagnetic valve (33a) are disconnected, and hydraulic oil in an oil path flows into the oil tank (45) through the unloading electromagnetic valve (33 a); when the unloading electromagnetic valve (33a) is closed, the oil inlet and the oil outlet of the unloading electromagnetic valve (33a) are communicated, hydraulic oil in the oil path cannot flow into the oil tank (45) through the unloading electromagnetic valve (33a),
the driving valve group (33) further comprises a two-way safety valve (33b), a first oil port of the two-way safety valve (33b) is respectively communicated with a first working oil port of the first hydraulic pump (32) and a plunger-free cavity of the first plunger cylinder (21), a second oil port of the two-way safety valve (33b) is respectively communicated with a second working oil port of the first hydraulic pump (32) and a plunger-free cavity of the second plunger cylinder (22), if hydraulic oil is discharged from the first working oil port of the first hydraulic pump (32), when the pressure of the first oil port of the two-way safety valve (33b) reaches a target pressure, the second oil port of the two-way safety valve (33b) is communicated with the first oil port to discharge the target flow rate of hydraulic oil, so that the pressure of the hydraulic oil in an oil path is reduced; if the second working oil port of the first hydraulic pump (32) discharges the hydraulic oil, when the pressure of the second oil port of the two-way safety valve (33b) reaches the target pressure, the second oil port of the two-way safety valve (33b) is communicated with the first oil port to discharge the hydraulic oil with the target flow rate, and the hydraulic oil pressure in the oil path is reduced.
2. The pump-controlled hydraulic steering engine of claim 1, wherein the pressure regulating valve block (44) further comprises a reversing valve (44c),
and a first oil inlet of the first pressure reduction overflow valve (44a) and a second oil inlet of the second pressure reduction overflow valve (44b) are respectively communicated with a rodless cavity of the piston oil cylinder (41) through the reversing valve (44 c).
3. The pump-controlled hydraulic steering engine according to claim 2, wherein a filter (44d) is arranged between the first oil outlet of the first pressure-reducing overflow valve (44a) and the oil tank (45) in communication, and between the second oil outlet of the second pressure-reducing overflow valve (44b) and the oil tank (45) in communication.
4. The pump-controlled hydraulic steering engine according to claim 1, characterized in that it further comprises a second oil-supplementing unit (5),
the second oil supply unit (5) comprises a first oil supply valve (51) and a second oil supply valve (52),
oil inlets of the first oil replenishing valve (51) and the second oil replenishing valve (52) are communicated with the oil tank (45), an oil outlet of the first oil replenishing valve (51) is communicated with a first working oil port of the first hydraulic pump (32) and a plunger-free cavity of the first plunger oil cylinder (21) respectively, and an oil outlet of the second oil replenishing valve (52) is communicated with a second working oil port of the first hydraulic pump (32) and a plunger-free cavity of the second plunger oil cylinder (22) respectively.
5. The pump-controlled hydraulic steering engine according to any one of claims 1 to 4, wherein said first electric motor (31) is a variable frequency motor.
6. The pump-controlled hydraulic steering engine according to claim 5, wherein the first hydraulic pump (32) is a fixed displacement pump.
7. Pump controlled hydraulic steering engine according to any one of claims 1-4, characterized in that the control unit is adapted to,
receiving a steering indication, wherein the steering indication comprises a target steering angle;
adjusting a rotation speed and a rotation direction of the first motor (31) based on the target rudder angle.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201910246952.4A CN110143271B (en) | 2019-03-29 | 2019-03-29 | Pump-controlled hydraulic steering engine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910246952.4A CN110143271B (en) | 2019-03-29 | 2019-03-29 | Pump-controlled hydraulic steering engine |
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| CN110143271A CN110143271A (en) | 2019-08-20 |
| CN110143271B true CN110143271B (en) | 2021-04-30 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP7409904B2 (en) * | 2020-02-28 | 2024-01-09 | 川崎重工業株式会社 | steering system |
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| CN108778925A (en) * | 2016-02-22 | 2018-11-09 | 三菱重工业株式会社 | Hydraulic steering gear and ship |
| CN208348187U (en) * | 2018-05-08 | 2019-01-08 | 凌云工业股份有限公司 | A kind of hydraulic press hydraulic control system equipped with synchronized cylinder |
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|---|---|---|---|---|
| GB734621A (en) * | 1953-02-09 | 1955-08-03 | Mactaggart Scott And Company L | Improvements in and relating to means for the remote control of ships' steering gear and other apparatus |
| JPS6020996U (en) * | 1983-07-22 | 1985-02-13 | 横河電機株式会社 | steering gear |
| JPS6021353Y2 (en) * | 1984-03-27 | 1985-06-25 | 株式会社トキメック | Steering control device |
| CN1123242A (en) * | 1994-10-10 | 1996-05-29 | 大连海事大学 | Unbalanced helming driving-torque imitating device |
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| CN110143271A (en) | 2019-08-20 |
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