A special valve group for large flow steering gear

Abstract

The present invention belongs to the field of ship technology and discloses a high-flow steering gear dedicated valve group, comprising a reversing valve, a double balancing valve, and a cartridge valve assembly. The reversing valve has a first oil port connected to an oil inlet of a hydraulic system, a second oil port connected to an oil return port of the hydraulic system, a third oil port connected to an oil output port of the first hydraulic system, and a fourth oil port connected to an oil output port of the second hydraulic system. The double balancing valve is connected in series between the third oil port and the oil output port of the first hydraulic system and between the fourth oil port and the oil output port of the second hydraulic system, respectively. The two ends of the cartridge valve assembly are connected to the oil output port of the first hydraulic system and the oil output port of the second hydraulic system, respectively. The high-flow steering gear dedicated valve group provided by the present invention has a double balancing valve that ensures that the reversing valve can maintain a positive load pressure even when the load is overloaded. Even if the load of the steering gear increases, the steering gear can still be stabilized at a set angle, thereby ensuring the steering gear's stable steering performance.

Description

Technical Field

[0001] The present invention relates to the technical field of ships, and in particular to a special valve group for a large-flow steering gear. Background Art

[0002] The marine hydraulic steering gear is the power source for manipulating the rotation of the rudder blades. The rotation of the rudder blades changes the navigation of the ship. That is, the action of the hydraulic steering gear determines the navigation and safety of the ship. Therefore, the hydraulic steering gear is one of the most important equipment on the ship.

[0003] The main types of hydraulic steering gear currently used on ships are: tilt-cylinder, scotch-yoke, and rotary vane. The tilt-cylinder electro-hydraulic steering gear uses a piston-type cylinder as the actuator, which rotates the tiller, thereby driving the rudder blades to achieve ship steering. When the steering gear outputs high torque, the cylinder stroke becomes very large, increasing the flow rate in the hydraulic system. Improper valve design can result in excessively high flow rates in the hydraulic system, causing a rapid increase in hydraulic system temperature, resulting in a significant pressure drop after the hydraulic oil passes through the valves. In severe cases, this can lead to steering gear failure, resulting in ship maneuverability issues and even collisions.

[0004] Therefore, there is an urgent need for a large-flow steering gear dedicated valve group to solve the above problems. Summary of the Invention

[0005] The object of the present invention is to provide a large-flow dedicated valve group for a steering gear. When the rudder is subjected to a load, the torque of the rudder exceeds the set output torque of the steering gear, which can unload the entire hydraulic system, prevent the entire hydraulic system from being overloaded, and protect the entire hydraulic system.

[0006] To achieve this object, the present invention adopts the following technical solutions:

[0007] A valve group dedicated to a large-flow steering gear includes a reversing valve, a double balancing valve and a cartridge valve assembly, wherein the first oil port of the reversing valve is connected to the oil inlet of the hydraulic system, the second oil port of the reversing valve is connected to the oil return port of the hydraulic system, the third oil port of the reversing valve is connected to the oil output port of the first hydraulic system, and the fourth oil port of the reversing valve is connected to the oil output port of the second hydraulic system. The double balancing valve is respectively connected in series between the third oil port and the oil output port of the first hydraulic system and between the fourth oil port and the oil output port of the second hydraulic system, and the two ends of the cartridge valve assembly are respectively connected to the oil output port of the first hydraulic system and the oil output port of the second hydraulic system.

[0008] Preferably, the double balancing valve includes a first balancing valve and a second balancing valve connected to the first balancing valve, one end of the first balancing valve is connected to the third oil port, the other end of the first balancing valve is connected to the first hydraulic system output oil port, one end of the second balancing valve is connected to the fourth oil port, and the other end of the second balancing valve is connected to the second hydraulic system output oil port.

[0009] Preferably, the cartridge valve assembly includes a first two-way cartridge valve, one oil port of the first two-way cartridge valve is connected to the first hydraulic system output oil port, and the other oil port of the first two-way cartridge valve is connected to the second hydraulic system output oil port.

[0010] Preferably, the control chamber of the first two-way cartridge valve is connected to a first control valve group, one oil port of the first control valve group is connected to the first hydraulic system output oil port, and the other oil port of the first control valve group is connected to the hydraulic oil port.

[0011] Preferably, the cartridge valve assembly also includes a second two-way cartridge valve, which is connected in parallel with the first two-way cartridge valve, one oil port of the second two-way cartridge valve is connected to the output oil port of the first hydraulic system, and the other oil port of the second two-way cartridge valve is connected to the output oil port of the second hydraulic system.

[0012] Preferably, the control chamber of the second two-way cartridge valve is connected to a second control valve group, one oil port of the second control valve group is connected to the second hydraulic system output oil port, and the other oil port of the second control valve group is connected to the hydraulic oil port.

[0013] Preferably, the reversing valve is a two-position four-way electro-hydraulic reversing valve, the electromagnetic reversing end of the reversing valve is connected to a pressure relay, and the hydraulic reversing end of the reversing valve is connected to a hydraulic oil port.

[0014] Preferably, the electromagnetic reversing end of the reversing valve is connected to a pressure measuring port.

[0015] Preferably, a high-pressure ball valve is further included, one end of the high-pressure ball valve is connected to the oil output port of the first hydraulic system, and the other end of the high-pressure ball valve is connected to the oil output port of the second hydraulic system.

[0016] Preferably, the third oil port is connected to the first communicating oil port and the second communicating oil port, and the fourth oil port is connected to the third communicating oil port and the fourth communicating oil port.

[0017] Beneficial effects of the present invention:

[0018] The high-flow, dedicated valve group for steering gears provided by the present invention utilizes a reversing valve to reverse the direction of the actuators in the entire hydraulic system. The dual balancing valve ensures that the reversing valve maintains a positive load pressure even when load overload occurs. This allows the steering gear to remain stable at the set angle even when the load increases, ensuring stable steering performance. When the rudder is subjected to significant external loads such as waves, currents, and other floating objects, and the rudder torque exceeds the set output torque of the steering gear, the cartridge valve assembly activates, unloading the entire hydraulic system, preventing overload and protecting the entire hydraulic system. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following briefly introduces the drawings required for use in describing the embodiments of the present invention. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the contents of the embodiments of the present invention and these drawings without any creative work.

[0020] Figure 1 This is a schematic diagram of the conduction connection principle of the large-flow steering gear special valve group provided by the present invention.

[0021] In the picture:

[0022] 100, reversing valve; 200, duplex balancing valve; 201, first balancing valve; 202, second balancing valve; 300, cartridge valve assembly; 301, first two-way cartridge valve; 302, first control valve group; 303, second two-way cartridge valve; 304, second control valve group; 400, pressure relay; 500, high-pressure ball valve;

[0023] P, hydraulic system oil inlet; T, hydraulic system oil return port; A1, first hydraulic system oil output port; B1, second hydraulic system oil output port; Y, hydraulic oil port; X, pressure measuring port; D1, first connecting oil port; D2, second connecting oil port; C1, third connecting oil port; C2, fourth connecting oil port; A, working oil inlet; B, working oil return port. DETAILED DESCRIPTION

[0024] The present invention will be further described in detail below with reference to the accompanying drawings and examples. It will be understood that the specific embodiments described herein are intended only to illustrate the present invention and are not intended to limit the present invention. It should also be noted that, for ease of description, the accompanying drawings only illustrate portions relevant to the present invention, not all structures.

[0025] In the description of the present invention, unless otherwise expressly specified or limited, the terms "connected," "connected," and "fixed" should be understood in a broad sense. For example, they may refer to fixed connections, detachable connections, or integration; mechanical connections or electrical connections; direct connections or indirect connections through an intermediate medium; and internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention in specific circumstances.

[0026] In the present invention, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Furthermore, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly below or obliquely below the second feature, or may simply mean that the first feature is lower in level than the second feature.

[0027] In the description of this embodiment, terms such as "upper," "lower," "left," and "right" are used to refer to positions or locations based on those shown in the accompanying drawings. These terms are intended solely to facilitate description and simplify operation, and are not intended to indicate or imply that the devices or components referred to must have, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limitations on the present invention. Furthermore, the terms "first" and "second" are used solely for descriptive purposes and have no special meaning.

[0028] like Figure 1 As shown, this embodiment provides a large-flow steering gear dedicated valve group, including a reversing valve 100, a double balancing valve 200 and a cartridge valve assembly 300, wherein the first oil port of the reversing valve 100 is connected to the hydraulic system oil inlet P, the second oil port of the reversing valve 100 is connected to the hydraulic system oil return port T, the third oil port of the reversing valve 100 is connected to the first hydraulic system output oil port A1, the fourth oil port of the reversing valve 100 is connected to the second hydraulic system output oil port B1, the double balancing 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 the two ends of the cartridge valve assembly 300 are respectively connected to the first hydraulic system output oil port A1 and the second hydraulic system output oil port B1.

[0029] The high-flow dedicated valve assembly for steering gears provided in this embodiment utilizes a reversing valve 100 to reverse the direction of the actuators in the entire hydraulic system. The dual balancing valve 200 ensures that the reversing valve 100 maintains a positive load pressure even when load overload occurs. This allows the steering gear to remain stable at the set angle even when the load increases, ensuring stable steering performance. When the rudder is subjected to significant external loads such as waves, currents, and other floating objects, and the rudder torque exceeds the set output torque of the steering gear, the cartridge valve assembly 300 activates, unloading the entire hydraulic system, preventing overload and protecting the entire hydraulic system.

[0030] The dual balancing valve 200 in this embodiment includes a first balancing valve 201 and a second balancing valve 202. The first balancing valve 201 is connected to the second balancing valve 202. One end of the first balancing valve 201 is connected to the third oil port, and the other end of the first balancing valve 201 is connected to the first hydraulic system output oil port A1. One end of the second balancing valve 202 is connected to the fourth oil port, and the other end of the second balancing valve 202 is connected to the second hydraulic system output oil port B1. The use of the dual balancing valve 200 ensures that the reversing valve 100 can maintain a positive load pressure even when the load exceeds the load. This is reflected in the operation of the steering gear: even if the load on the steering gear increases, the steering gear can still be stabilized at the set angle, improving the steering gear's stabilization performance. This embodiment uses the dual balancing valve 200 instead of a conventional hydraulic lock, avoiding the over-relaxation phenomenon of the steering gear, overcoming the "negative torque" phenomenon that may be generated by the rudder blade during operation, and improving the stabilization performance of the marine hydraulic steering gear.

[0031] As a preferred technical solution, the double balancing valve 200 can be but is not limited to a plug-in type. By adopting the plug-in type double balancing valve 200, the volume of the valve group dedicated to large-flow steering gear can be greatly reduced, the footprint of the electric hydraulic steering gear valve group can be reduced, and the degree of system integration can be increased.

[0032] The cartridge valve assembly 300 in this embodiment includes a first two-way cartridge valve 301. One port of the first two-way cartridge valve 301 is connected to the first hydraulic system output port A1, and the other port of the first two-way cartridge valve 301 is connected to the second hydraulic system output port B1. This structure enables the first two-way cartridge valve 301 to function as a safety valve in conjunction with a cover plate for high-pressure relief control. When the rudder is subjected to significant external loads such as waves, currents, and other floating objects, and the rudder torque exceeds the set output torque of the steering gear, the first two-way cartridge valve 301 activates, unloading the entire hydraulic system, preventing overload and protecting the entire hydraulic system.

[0033] Optionally, in a specific embodiment, the control chamber of the first two-way cartridge valve 301 is connected to a first control valve group 302, one oil port of the first control valve group 302 is connected to the first hydraulic system output port A1, and the other oil port of the first control valve group 302 is connected to the hydraulic port Y. This structure facilitates control of the first two-way cartridge valve 301 and facilitates unloading of the entire hydraulic system. Furthermore, when connected to the hydraulic port Y, an external control mode is established, which is unaffected by the hydraulic system. As a preferred technical solution, the other oil port of the first control valve group 302 is connected to the end of the first hydraulic system output port A1 near the first balancing valve 201 and the end of the second hydraulic system output port B1 near the second balancing valve 202. This structure establishes an internal control mode. When used in conjunction with the external control mode described above, the control mode can be adjusted to internal or external control as needed, making adjustment convenient.

[0034] Furthermore, in one embodiment, the cartridge valve assembly 300 further includes a second two-way cartridge valve 303, which is connected in parallel with the first two-way cartridge valve 301. One port of the second two-way cartridge valve 303 is connected to the first hydraulic system output port A1, and the other port of the second two-way cartridge valve 303 is connected to the second hydraulic system output port B1. With this structure, the second two-way cartridge valve 303 can cooperate with the cover plate of the high-pressure relief control function to form a safety valve. When the rudder is subjected to excessive external loads such as waves, currents, and other floating objects, and the rudder torque exceeds the set output torque of the steering gear, the first two-way cartridge valve 301 or the second two-way cartridge valve 303 activates, unloading the entire hydraulic system, preventing overload and protecting the entire hydraulic system. Furthermore, the coordinated use of the first two-way cartridge valve 301 and the second two-way cartridge valve 303 enhances the unloading effect on the hydraulic system.

[0035] Optionally, in one specific embodiment, the control chamber of the second two-way cartridge valve 303 is connected to a second control valve assembly 304. One oil port of the second control valve assembly 304 is connected to the second hydraulic system output port B1, and the other oil port of the second control valve assembly 304 is connected to hydraulic port Y. This structure facilitates control of the second two-way cartridge valve 303 and facilitates unloading of the entire hydraulic system. Furthermore, when connected to hydraulic port Y, it forms an external control mode, unaffected by the hydraulic system. As a preferred technical solution, the other oil port of the second control valve assembly 304 is connected to the end of the first hydraulic system output port A1 near the first balancing valve 201 and the end of the second hydraulic system output port B1 near the second balancing valve 202. This structure forms an internal control mode. When used in conjunction with the external control mode described above, the control mode can be adjusted to internal or external control as needed, making adjustment convenient.

[0036] The high-flow dedicated valve group for steering gears provided in this embodiment increases the flow rate of the hydraulic system and reduces the pressure drop of the hydraulic system through the valve components by adopting the first two-way cartridge valve 301 and the second two-way cartridge valve 303. At the same time, the volume of the high-flow dedicated valve group for steering gears is greatly reduced, the footprint of the electric hydraulic steering gear valve group is reduced, and the degree of system integration is high.

[0037] 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 to a pressure relay 400 , and the hydraulic reversing end of the reversing valve 100 is connected to the hydraulic oil port Y. The two-position, four-way electro-hydraulic reversing valve has an automatic reset function and can reverse the direction of the actuators of the entire hydraulic system. The pressure relay 400 monitors the operation of the entire hydraulic system and issues an audible and visual alarm when the system pressure is too low.

[0038] Optionally, in a specific embodiment, the electromagnetic reversing end of the reversing valve 100 is connected to a pressure measuring port X. By providing the pressure measuring port X, the operation of the entire hydraulic system can be monitored easily.

[0039] The high-flow servo-specific valve assembly provided in this embodiment also includes a high-pressure ball valve 500, one end of which is connected to the first hydraulic system oil output port A1, and the other end of which is connected to the second hydraulic system oil output port B1. By connecting the first hydraulic system oil output port A1 and the second hydraulic system oil output port B1, the high-pressure ball valve 500 is normally closed. In the event of a hydraulic system failure, the high-pressure ball valve 500 can be opened, thereby connecting the first hydraulic system oil output port A1 with the second hydraulic system oil output port B1 and isolating the actuators connected to the first and second hydraulic system oil output ports A1 and B1.

[0040] In this embodiment, the third oil port is connected to the first and second oil ports D1 and D2, and the fourth oil port is connected to the third and fourth oil ports C1 and C2. This structure provides two hydraulic systems for the steering gear, which operate in a "one active, one standby" mode. The two hydraulic systems are connected in parallel via the first and second oil ports D1 and D2, and the third and fourth oil ports C1 and C2. If one hydraulic system fails, the faulty system can be isolated via the first and second oil ports D1 and D2, and the third and fourth oil ports C1 and C2.

[0041] In this embodiment, the hydraulic system oil inlet P is connected to the working oil inlet A, and the hydraulic system oil return port T is connected to the working oil return port B.

[0042] Obviously, the above embodiments of the present invention are merely examples for the purpose of clearly illustrating the present invention and are not intended to limit the embodiments of the present invention. A person skilled in the art would be able to make various obvious changes, readjustments, and substitutions without departing from the scope of protection of the present invention. It is not necessary and impossible to enumerate all embodiments here. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention shall be included within the scope of protection of the claims of the present invention.

Claims

1. A large flow steering gear dedicated valve group, characterized in that: The invention comprises a reversing valve (100), a double balancing valve (200) and a cartridge valve assembly (300), wherein the first oil port of the reversing valve (100) is connected to the oil inlet (P) of the hydraulic system, the second oil port of the reversing valve (100) is connected to the oil return port (T) of the hydraulic system, the third oil port of the reversing valve (100) is connected to the oil output port (A1) of the first hydraulic system, and the fourth oil port of the reversing valve (100) is connected to the oil output port (B1) of the second hydraulic system. The double balancing valve (200) is connected in series between the third oil port and the oil output port (A1) of the first hydraulic system and between the fourth oil port and the oil output port (B1) of the second hydraulic system, respectively. The two ends of the cartridge valve assembly (300) are connected to the oil output port (A1) of the first hydraulic system and the oil output port (B1) of the second hydraulic system respectively. The double balancing valve (200) comprises a first balancing valve (201) and a second balancing valve (202) connected to the first balancing valve (201), one end of the first balancing valve (201) is connected to the third oil port, the other end of the first balancing valve (201) is connected to the first hydraulic system output oil port (A1), one end of the second balancing valve (202) is connected to the fourth oil port, and the other end of the second balancing valve (202) is connected to the second hydraulic system output oil port (B1); The cartridge valve assembly (300) comprises a first two-way cartridge valve (301), one oil port of the first two-way cartridge valve (301) being connected to the first hydraulic system output oil port (A1), and the other oil port of the first two-way cartridge valve (301) being connected to the second hydraulic system output oil port (B1); The control chamber of the first two-way cartridge valve (301) is connected to a first control valve group (302), one oil port of the first control valve group (302) is connected to the first hydraulic system output oil port (A1), and the other oil port of the first control valve group (302) is connected to the hydraulic oil port (Y); The cartridge valve assembly (300) further comprises a second two-way cartridge valve (303), the second two-way cartridge valve (303) being connected in parallel with the first two-way cartridge valve (301), one oil port of the second two-way cartridge valve (303) being connected to the first hydraulic system output oil port (A1), and the other oil port of the second two-way cartridge valve (303) being connected to the second hydraulic system output oil port (B1); The control chamber of the second two-way cartridge valve (303) is connected to a second control valve group (304), one oil port of the second control valve group (304) is connected to the second hydraulic system output oil port (B1), and the other oil port of the second control valve group (304) is connected to the hydraulic oil port (Y).

2. The high flow rate dedicated valve group for steering gear according to claim 1, characterized in that: 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 to a pressure relay (400), and the hydraulic reversing end of the reversing valve (100) is connected to a hydraulic oil port (Y).

3. The high flow rate dedicated valve group for steering gear according to claim 2, characterized in that: The electromagnetic reversing end of the reversing valve (100) is connected to a pressure measuring port (X).

4. The high flow rate dedicated valve group for steering gear according to claim 1, characterized in that: It also includes a high-pressure ball valve (500), one end of which is connected to the first hydraulic system oil output port (A1), and the other end of which is connected to the second hydraulic system oil output port (B1).

5. The high flow rate dedicated valve group for steering gear according to any one of claims 1 to 4, characterized in that: The third oil port is connected to the first communicating oil port (D1) and the second communicating oil port (D2), and the fourth oil port is connected to the third communicating oil port (C1) and the fourth communicating oil port (C2).

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