CN113638929A - Compact type valve bank special for steering engine - Google Patents
Compact type valve bank special for steering engine Download PDFInfo
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- CN113638929A CN113638929A CN202111069530.8A CN202111069530A CN113638929A CN 113638929 A CN113638929 A CN 113638929A CN 202111069530 A CN202111069530 A CN 202111069530A CN 113638929 A CN113638929 A CN 113638929A
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- valve
- oil port
- hydraulic system
- port
- system output
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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
- 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
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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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- 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
- F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
- F15B2013/004—Cartridge valves
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Ocean & Marine Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention belongs to the technical field of ships and discloses a compact valve group special for a steering engine, which comprises a valve plate, a reversing valve, a duplex balance valve and a cartridge valve component, wherein the reversing valve, the duplex balance valve and the cartridge valve component are arranged on the valve plate, the valve plate is provided with a hydraulic system oil inlet and a hydraulic system oil return port, the hydraulic control system comprises a first hydraulic system output oil port, a second hydraulic system output oil port and a hydraulic oil port, wherein the first oil port of a reversing valve is connected with an oil inlet of the hydraulic system, the second oil port is connected with an oil return port of the hydraulic system, the third oil port is connected with the first hydraulic system output oil port, the fourth oil port is connected with the second hydraulic system output oil port, a duplex balance valve is respectively connected between the third oil port and the first hydraulic system output oil port and between the fourth oil port and the second hydraulic system output oil port in series, and two ends of a cartridge valve assembly are respectively connected with the first hydraulic system output oil port and the second hydraulic system output oil port. This special valves of compact steering wheel volume is littleer, and the product integrates the degree higher, and area is littleer.
Description
Technical Field
The invention relates to the technical field of ships, in particular to a compact valve bank special for a steering engine.
Background
The marine hydraulic steering engine is a power source for controlling the rotation of the rudder blade, so that the navigation of the ship is changed due to the rotation of the rudder blade, namely the navigation and the safety of the ship are determined by the action of the hydraulic steering engine, and the hydraulic steering engine is one of the most important devices on the ship.
The hydraulic steering engine steering wheel that uses on present boats and ships mainly is: a tilt cylinder type, a shift fork type and a rotary vane type. The oscillating cylinder type electro-hydraulic steering engine adopts a piston type oil cylinder as an actuating mechanism to push the rudder tiller to rotate, so that the rudder blade is driven to rotate, and the steering of a ship is realized. When the output rotation torque of the steering engine is large, the stroke of the oil cylinder is very large, and the flow of the hydraulic system is increased. If the valve member is selected not to design, then can cause hydraulic system velocity of flow too high, hydraulic system temperature risees very fast, leads to the pressure drop behind the valve member of hydraulic oil great, and when the condition was serious, then can lead to the steering wheel to become invalid to take place boats and ships and control malfunctioning, the condition of boats and ships collision takes place, and current valve member integrates the degree in addition lowly, leads to area great.
Therefore, a compact valve set dedicated for a steering engine is needed to solve the above problems.
Disclosure of Invention
The invention aims to provide a compact valve group special for a steering engine, which has higher integration degree and smaller occupied area, and when the rudder is loaded, the torque of the rudder exceeds the set output torque of the steering engine, so that the whole hydraulic system can be unloaded, the whole hydraulic system is prevented from being overloaded, and the whole hydraulic system is protected.
In order to achieve the purpose, the invention adopts the following technical scheme:
a compact valve group special for a steering engine comprises a reversing valve, a duplex balance valve, a cartridge valve assembly and a valve plate, wherein the reversing valve, the duplex balance valve and the cartridge valve assembly are arranged on the valve plate, a hydraulic system oil inlet, a hydraulic system oil return port, a first hydraulic system output oil port, a second hydraulic system output oil port and a hydraulic oil port are formed in the valve plate, a first oil port of the reversing valve is connected with the hydraulic system oil inlet, a second oil port of the reversing valve is connected with the hydraulic system oil return port, a third oil port of the reversing valve is connected with the first hydraulic system output oil port, a fourth oil port of the reversing valve is connected with the second hydraulic system output oil port, the duplex balance valve is respectively connected in series between the third oil port and the first hydraulic system output oil port and between the fourth oil port and the second hydraulic system output oil port, and two ends of the plug-in valve assembly are respectively connected with the output oil port of the first hydraulic system and the output oil port of the second hydraulic system.
Preferably, the double balance valve includes a first balance valve and a second balance valve connected to the first balance valve, the first balance valve and the second balance valve are disposed on the valve plate, one end of the first balance valve is connected to the third oil port, the other end of the first balance valve is connected to the first hydraulic system output oil port, one end of the second balance valve is connected to the fourth oil port, and the other end of the second balance valve is connected to the second hydraulic system output oil port.
Preferably, the cartridge valve assembly comprises a first two-way cartridge valve, the first two-way cartridge valve is arranged on the valve plate, one oil port of the first two-way cartridge valve is connected with the output oil port of the first hydraulic system, and the other oil port of the first two-way cartridge valve is connected with the output oil port of the second hydraulic system.
Preferably, a control cavity of the first two-way cartridge valve is connected with a first control valve group, one oil port of the first control valve group is connected with an output oil port of the first hydraulic system, and the other oil port of the first control valve group is connected with the hydraulic oil port.
Preferably, the cartridge valve assembly further comprises a second two-way cartridge valve, the second two-way cartridge valve is arranged on the valve plate, the second two-way cartridge valve is connected with the first two-way cartridge valve in parallel, one oil port of the second two-way cartridge valve is connected with the output oil port of the first hydraulic system, and the other oil port of the second two-way cartridge valve is connected with the output oil port of the second hydraulic system.
Preferably, a control cavity of the second two-way cartridge valve is connected with a second control valve group, one oil port of the second control valve group is connected with an output oil port of the second hydraulic system, and the other oil port of the second control valve group is connected with the hydraulic oil port.
Preferably, the reversing valve is a two-position four-way electro-hydraulic reversing valve, the electromagnetic reversing end of the reversing valve is connected with a pressure relay, the pressure relay is arranged on the valve plate, and the hydraulic reversing end of the reversing valve is connected with the hydraulic oil port.
Preferably, the valve plate is provided with a pressure measuring port, and the electromagnetic reversing end of the reversing valve is connected with the pressure measuring port.
Preferably, the hydraulic control valve further comprises a high-pressure ball valve, the high-pressure ball valve is arranged on the valve plate, one end of the high-pressure ball valve is connected with the output oil port of the first hydraulic system, and the other end of the high-pressure ball valve is connected with the output oil port of the second hydraulic system.
Preferably, a first communicating oil port, a second communicating oil port, a third communicating oil port and a fourth communicating oil port are further formed in the valve plate, the third oil port is connected with the first communicating oil port and the second communicating oil port, the first communicating oil port is connected with the second communicating oil port in parallel, the fourth oil port is connected with the third communicating oil port and the fourth communicating oil port, and the third communicating oil port is connected with the fourth communicating oil port in parallel.
The invention has the beneficial effects that:
according to the compact valve bank special for the steering engine, the valve plate and the plug-in valve assembly are arranged, so that the volume of the valve bank can be effectively reduced, the integration degree of a product is higher, the occupied area of the product is smaller, when the rudder is subjected to extra-large external loads such as waves, ocean currents and other floaters, the torque of the rudder exceeds the set output torque of the steering engine, the plug-in valve assembly works, the whole hydraulic system is unloaded, the whole hydraulic system is prevented from being overloaded, and the whole hydraulic system is protected; by arranging the reversing valve, the actuating mechanism of the whole hydraulic system can be reversed; the duplex balance valve ensures that the reversing valve can be under positive load pressure when the load is in an over-relaxation phenomenon, and the steering engine can be still stabilized at a set angle even if the load of the steering engine is increased, so that the steering stabilizing performance of the steering engine is ensured.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings used in the description of the embodiments of the present invention will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the contents of the embodiments of the present invention and the drawings without creative efforts.
FIG. 1 is a first structural schematic diagram of a compact type steering engine special valve bank provided by the invention;
FIG. 2 is a schematic structural diagram II of the compact steering engine dedicated valve bank provided by the invention;
fig. 3 is a conducting connection schematic diagram of the compact steering engine special valve bank provided by the invention.
In the figure:
100. a diverter valve; 200. a double balanced valve; 201. a first counter-balance valve; 202. a second balancing valve; 300. a valve assembly is inserted; 301. a first two-way cartridge valve; 302. a first control valve group; 303. a second two-way cartridge valve; 304. a second control valve group; 400. a valve plate; 500. a pressure relay; 600. a high pressure ball valve;
p, an oil inlet of a hydraulic system; t, an oil return port of the hydraulic system; a1, a first hydraulic system output oil port; b1, a second hydraulic system output oil port; y, a hydraulic oil port; x, a pressure measuring port; d1, a first communication oil port; d2 and a second communication oil port; c1, a third communicating oil port; c2, a fourth communication oil port; A. a working oil inlet; B. and a working oil return port.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and examples. It is to be understood that the specific embodiments described herein are merely illustrative of the invention and are not limiting of the invention. It should be further noted that, for the convenience of description, only some of the structures related to the present invention are shown in the drawings, not all of the structures.
In the description of the present invention, unless expressly stated or limited otherwise, the terms "connected," "connected," and "fixed" are to be construed broadly, e.g., as meaning permanently connected, removably connected, or integral to one another; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
In the description of the present embodiment, the terms "upper", "lower", "left", "right", and the like are used based on the orientations and positional relationships shown in the drawings only for convenience of description and simplification of operation, and do not indicate or imply that the referred device or element must have a specific orientation, be configured and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used only for descriptive purposes and are not intended to have a special meaning.
As shown in fig. 1 to 3, the embodiment provides a compact valve set dedicated for a steering engine, including a directional control valve 100, a double-link balance valve 200, a cartridge valve assembly 300, and a valve plate 400, where the directional control valve 100, the double-link balance valve 200, and the cartridge valve assembly 300 are disposed on the valve plate 400, the valve plate 400 is provided with a hydraulic system oil inlet P, a hydraulic system oil return port T, a first hydraulic system output port a1, a second hydraulic system output port B1, and a hydraulic port Y, a first oil port of the directional control valve 100 is connected to the hydraulic system oil inlet P, a second oil port of the directional control valve 100 is connected to the hydraulic system oil return port T, a third oil port of the directional control valve 100 is connected to the first hydraulic system output port a1, a fourth oil port of the directional control valve 100 is connected to the second hydraulic system output port B1, the double-link balance valve 200 is respectively connected in series between the third oil port and the first hydraulic system output port a1, and between the fourth oil port and the second hydraulic system output port B1, both ends of the cartridge valve assembly 300 are connected to the first hydraulic system outlet port a1 and the second hydraulic system outlet port B1, respectively.
According to the compact valve bank special for the steering engine, the valve plate 400 and the cartridge valve assembly 300 are arranged, so that the volume of the valve bank can be effectively reduced, the integration degree of a product is higher, the occupied area of the product is smaller, when the rudder is subjected to extra-large external loads such as waves, ocean currents and other floaters, the torque of the rudder exceeds the set output torque of the steering engine, the cartridge valve assembly 300 works, the whole hydraulic system is unloaded, the whole hydraulic system is prevented from being overloaded, and the whole hydraulic system is protected; by arranging the reversing valve 100, the actuating mechanism of the whole hydraulic system can be reversed; the double balance valve 200 ensures that the reversing valve 100 can be under positive load pressure when the load is in an over-relaxation phenomenon, and the steering engine can be still stabilized at a set angle even if the load of the steering engine is increased, so that the steering stability of the steering engine is ensured.
The double balanced valve 200 in this embodiment includes a first balanced valve 201 and a second balanced valve 202, the first balanced valve 201 and the second balanced valve 202 are disposed on the valve plate 400, the first balanced valve 201 is connected to the second balanced valve 202, one end of the first balanced valve 201 is connected to the third oil port, the other end of the first balanced valve 201 is connected to the first hydraulic system output oil port a1, one end of the second balanced valve 202 is connected to the fourth oil port, and the other end of the second balanced valve 202 is connected to the second hydraulic system output oil port B1. By using the dual trim valve 200, the reversing valve 100 is assured of being at a positive load pressure even when the load experiences an overshoot. The steering engine is embodied in the following working phenomena: even if the load of the steering engine is increased, the steering engine can still be stabilized at a set angle, and the steering stabilizing performance of the steering engine is improved. In the embodiment, the duplex balance valve 200 is adopted to replace a conventional hydraulic lock, the phenomenon of over-relaxation of the steering engine is avoided, the phenomenon of negative torque possibly generated by the rudder blade in the operation process is overcome, and the rudder stabilizing performance of the marine hydraulic steering engine is improved.
As an optimal technical scheme, the double balance valve 200 can be but not limited to a plug-in type, and the plug-in type double balance valve 200 is adopted, so that the size of the compact type steering engine special valve bank can be greatly reduced, the occupied area of the electro-hydraulic steering engine valve bank is reduced, and the system integration degree is increased.
The cartridge valve assembly 300 in the embodiment comprises a first two-way cartridge valve 301, the first two-way cartridge valve 301 is arranged on the valve plate 400, one oil port of the first two-way cartridge valve 301 is connected with a first hydraulic system output oil port A1, and the other oil port of the first two-way cartridge valve 301 is connected with a second hydraulic system output oil port B1. Through the structure, the first two-way cartridge valve 301 can be matched with a cover plate with a high-pressure overflow control function to form a safety valve. When the rudder is subjected to extra-large external loads such as waves, ocean currents and other floaters, the torque of the rudder exceeds the set output torque of the steering engine, the first two-way cartridge valve 301 works to unload the whole hydraulic system, the whole hydraulic system is prevented from being overloaded, and the whole hydraulic system is protected.
Optionally, in a specific embodiment, a first control valve block 302 is connected to the control chamber of the first two-way cartridge valve 301, one port of the first control valve block 302 is connected to the first hydraulic system outlet port a1, and the other port of the first control valve block 302 is connected to the hydraulic port Y. Through the structure, the first two-way cartridge valve 301 can be conveniently controlled, and the whole hydraulic system can be conveniently unloaded; and after being connected with the hydraulic oil port Y, the hydraulic oil port Y forms an external control type and can not be influenced by a hydraulic system. As a preferable technical solution, the other port of the first control valve group 302 is connected to one end of the first hydraulic system output port a1 close to the first balanced valve 201 and one end of the second hydraulic system output port B1 close to the second balanced valve 202, and by the above structure, an internal control type is formed, and the internal control type is used in cooperation with the external control type, so that the control mode can be adjusted to the internal control type or the external control type as required, and the adjustment is convenient.
In one embodiment, the cartridge valve assembly 300 further comprises a second two-way cartridge 303, the second two-way cartridge 303 is arranged on the valve plate 400, the second two-way cartridge 303 is connected with the first two-way cartridge 301 in parallel, one port of the second two-way cartridge 303 is connected with the first hydraulic system outlet port a1, and the other port of the second two-way cartridge 303 is connected with the second hydraulic system outlet port B1. Through the structure, the second two-way cartridge valve 303 can be matched with a cover plate with a high-pressure overflow control function to form a safety valve. When the rudder is subjected to extra-large external loads such as waves, ocean currents and other floaters, the torque of the rudder exceeds the set output torque of the steering engine, the first two-way cartridge valve 301 or the second two-way cartridge valve 303 works to unload the whole hydraulic system, so that the whole hydraulic system is prevented from being overloaded, and is protected; and the first two-way cartridge valve 301 and the second two-way cartridge valve 303 are matched for use, so that the unloading effect of the hydraulic system is improved.
Optionally, in a specific embodiment, a second control valve block 304 is connected to the control chamber of the second two-way cartridge valve 303, one port of the second control valve block 304 is connected to the second hydraulic system outlet port B1, and the other port of the second control valve block 304 is connected to the hydraulic port Y. Through the structure, the second two-way cartridge valve 303 can be conveniently controlled, and the whole hydraulic system can be conveniently unloaded; and after being connected with the hydraulic oil port Y, the hydraulic oil port Y forms an external control type and can not be influenced by a hydraulic system. As a preferable technical solution, the other port of the second control valve group 304 is connected to one end of the first hydraulic system output port a1 close to the first balanced valve 201 and one end of the second hydraulic system output port B1 close to the second balanced valve 202, and by the above structure, an internal control type is formed, and the control mode can be adjusted to the internal control type or the external control type as required, so that the adjustment is convenient.
The special valves of compact steering wheel that this embodiment provided is through adopting first two-way cartridge valve 301 and second two-way cartridge valve 303, has increased hydraulic system's logical flow, reduces the pressure drop that hydraulic system passes through the valve member, and first two-way cartridge valve 301 and second two-way cartridge valve 303 set up on valve plate 400 simultaneously, make the volume of this special valves of compact steering wheel reduce by a wide margin, make electronic hydraulic steering wheel valves area reduce, and the degree of integrating of system is high.
The reversing valve 100 in this embodiment is a two-position four-way electro-hydraulic reversing valve, the electromagnetic reversing end of the reversing valve 100 is connected with a pressure relay 500, and the hydraulic reversing end of the reversing valve 100 is connected with a hydraulic oil port Y. The two-position four-way electro-hydraulic reversing valve has an automatic resetting function and can reverse an actuating mechanism of the whole hydraulic system; through setting up pressure relay 500, can monitor whole hydraulic system's operational aspect, when the pressure of system is low excessively, send audible and visual alarm.
Optionally, in a specific embodiment, the electromagnetic reversing end of the reversing valve 100 is connected to a pressure measuring port X, and by providing the pressure measuring port X, the operation condition of the whole hydraulic system is conveniently monitored.
The special valve bank of compact steering wheel that this embodiment provided still includes high-pressure ball valve 600, and high-pressure ball valve 600 sets up on valve plate 400, and wherein, the one end and the first hydraulic system output oil port A1 of high-pressure ball valve 600 are connected, and the other end and the second hydraulic system output oil port B1 of high-pressure ball valve 600 are connected moreover. By arranging the high-pressure ball valve 600 on the valve plate 400, the high-pressure ball valve 600 is connected with the first hydraulic system output oil port a1 and the second hydraulic system output oil port B1, and the high-pressure ball valve 600 is in a closed state under normal conditions. When the hydraulic system fails, the high-pressure ball valve 600 may be opened, so that the first hydraulic system output port a1 is communicated with the second hydraulic system output port B1, and the actuator connected to the first hydraulic system output port a1 and the second hydraulic system output port B1 is isolated.
The valve plate 400 in this embodiment is further provided with a first communicating oil port D1, a second communicating oil port D2, a third communicating oil port C1 and a fourth communicating oil port C2, wherein the first communicating oil port D1 and the second communicating oil port D2 are connected to the third oil port, the first communicating oil port D1 is connected to the second communicating oil port D2 in parallel, the third communicating oil port C1 and the fourth communicating oil port C2 are connected to the fourth oil port, and the third communicating oil port C1 is connected to the fourth communicating oil port C2 in parallel. Through the structure, the hydraulic systems of the steering engine are provided with two sets, and a working mode of one set and one spare set is adopted in the using process. The two sets of hydraulic systems are connected in parallel by arranging the first communicating oil port D1, the second communicating oil port D2, the third communicating oil port C1 and the fourth communicating oil port C2, and when one set of hydraulic system breaks down, the broken hydraulic system can be isolated by the first communicating oil port D1, the second communicating oil port D2, the third communicating oil port C1 and the fourth communicating oil port C2.
As an optimized technical scheme, the valve plate 400 is further provided with a working oil inlet a and a working oil return port B, the hydraulic system oil inlet P is connected with the working oil inlet a, and the hydraulic system oil return port T is connected with the working oil return port B.
It should be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Numerous obvious variations, adaptations and substitutions will occur to those skilled in the art without departing from the scope of the invention. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.
Claims (10)
1. The compact valve group special for the steering engine is characterized by comprising a reversing valve (100), a duplex balance valve (200), a cartridge valve assembly (300) and a valve plate (400), wherein the reversing valve (100), the duplex balance valve (200) and the cartridge valve assembly (300) are arranged on the valve plate (400), a hydraulic system oil inlet (P), a hydraulic system oil return port (T), a first hydraulic system output oil port (A1), a second hydraulic system output oil port (B1) and a hydraulic oil port (Y) are formed in the valve plate (400), a first oil port of the reversing valve (100) is connected with the hydraulic system oil inlet (P), a second oil port of the reversing valve (100) is connected with the hydraulic system oil return port (T), a third oil port of the reversing valve (100) is connected with the first hydraulic system output oil port (A1), the fourth oil port of the reversing valve (100) is connected with the second hydraulic system output oil port (B1), the double-linkage balance valve (200) is respectively connected in series between the third oil port and the first hydraulic system output oil port (A1) and between the fourth oil port and the second hydraulic system output oil port (B1), and two ends of the cartridge valve assembly (300) are respectively connected with the first hydraulic system output oil port (A1) and the second hydraulic system output oil port (B1).
2. The compact valve bank dedicated for the steering engine as claimed in claim 1, wherein the double balance valve (200) comprises a first balance valve (201) and a second balance valve (202) connected with the first balance valve (201), the first balance valve (201) and the second balance valve (202) are arranged on the valve plate (400), one end of the first balance valve (201) is connected with the third oil port, the other end of the first balance valve (201) is connected with the first hydraulic system output oil port (A1), one end of the second balance valve (202) is connected with the fourth oil port, and the other end of the second balance valve (202) is connected with the second hydraulic system output oil port (B1).
3. The compact valve group special for the steering engine as claimed in claim 1, wherein the cartridge valve assembly (300) comprises a first two-way cartridge valve (301), the first two-way cartridge valve (301) is arranged on the valve plate (400), one oil port of the first two-way cartridge valve (301) is connected with the first hydraulic system output oil port (A1), and the other oil port of the first two-way cartridge valve (301) is connected with the second hydraulic system output oil port (B1).
4. The compact valve bank special for the steering engine as claimed in claim 3, wherein a control cavity of the first two-way cartridge valve (301) is connected with a first control valve bank (302), one oil port of the first control valve bank (302) is connected with the first hydraulic system output oil port (A1), and the other oil port of the first control valve bank (302) is connected with the hydraulic oil port (Y).
5. The compact valve group special for the steering engine as claimed in claim 3, wherein the cartridge valve assembly (300) further comprises a second two-way cartridge valve (303), the second two-way cartridge valve (303) is arranged on the valve plate (400), the second two-way cartridge valve (303) is connected with the first two-way cartridge valve (301) in parallel, one oil port of the second two-way cartridge valve (303) is connected with the first hydraulic system output oil port (A1), and the other oil port of the second two-way cartridge valve (303) is connected with the second hydraulic system output oil port (B1).
6. The compact valve bank special for the steering engine as claimed in claim 5, wherein a control cavity of the second two-way cartridge valve (303) is connected with a second control valve bank (304), one oil port of the second control valve bank (304) is connected with the second hydraulic system output oil port (B1), and the other oil port of the second control valve bank (304) is connected with the hydraulic oil port (Y).
7. The compact type valve bank special for the steering engine as claimed in claim 1, wherein the reversing valve (100) is a two-position four-way electro-hydraulic reversing valve, the electromagnetic reversing end of the reversing valve (100) is connected with a pressure relay (500), the pressure relay (500) is arranged on the valve plate (400), and the hydraulic reversing end of the reversing valve (100) is connected with the hydraulic oil port (Y).
8. The compact valve group special for the steering engine as claimed in claim 7, wherein a pressure measuring port (X) is formed in the valve plate (400), and the electromagnetic reversing end of the reversing valve (100) is connected with the pressure measuring port (X).
9. The compact valve group special for the steering engine according to claim 1, further comprising a high-pressure ball valve (600), wherein the high-pressure ball valve (600) is arranged on the valve plate (400), one end of the high-pressure ball valve (600) is connected with the first hydraulic system output oil port (A1), and the other end of the high-pressure ball valve (600) is connected with the second hydraulic system output oil port (B1).
10. The compact valve group special for the steering engine as claimed in claim 1, wherein the valve plate (400) is further provided with a first communicating oil port (D1), a second communicating oil port (D2), a third communicating oil port (C1) and a fourth communicating oil port (C2), the third oil port is connected with the first communicating oil port (D1) and the second communicating oil port (D2), the first communicating oil port (D1) is connected in parallel with the second communicating oil port (D2), the fourth oil port is connected with the third communicating oil port (C1) and the fourth communicating oil port (C2), and the third communicating oil port (C1) is connected in parallel with the fourth communicating oil port (C2).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111069530.8A CN113638929A (en) | 2021-09-13 | 2021-09-13 | Compact type valve bank special for steering engine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111069530.8A CN113638929A (en) | 2021-09-13 | 2021-09-13 | Compact type valve bank special for steering engine |
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| CN113638929A true CN113638929A (en) | 2021-11-12 |
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| CN202111069530.8A Pending CN113638929A (en) | 2021-09-13 | 2021-09-13 | Compact type valve bank special for steering engine |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114222867A (en) * | 2021-11-15 | 2022-03-22 | 无锡市东舟船舶设备股份有限公司 | Valve group |
| CN115523203A (en) * | 2022-09-14 | 2022-12-27 | 南京航海仪器二厂有限公司 | Rotary vane steering engine steering oil cylinder fault isolation valve bank and rotary vane steering engine |
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2021
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114222867A (en) * | 2021-11-15 | 2022-03-22 | 无锡市东舟船舶设备股份有限公司 | Valve group |
| WO2023082233A1 (en) * | 2021-11-15 | 2023-05-19 | 无锡市东舟船舶设备股份有限公司 | Valve group |
| CN115523203A (en) * | 2022-09-14 | 2022-12-27 | 南京航海仪器二厂有限公司 | Rotary vane steering engine steering oil cylinder fault isolation valve bank and rotary vane steering engine |
| CN115523203B (en) * | 2022-09-14 | 2023-09-15 | 南京航海仪器二厂有限公司 | Rotary vane steering engine rudder oil cylinder fault isolation valve group and rotary vane steering engine |
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