A compact valve group for steering gear

Abstract

The present invention belongs to the field of ship technology, and discloses a compact steering gear special valve group, including a valve plate and a reversing valve, a double balance valve and a cartridge valve assembly arranged on the valve plate, the valve plate is provided with a hydraulic system oil inlet, a hydraulic system oil return port, a first hydraulic system oil output port, a second hydraulic system oil output port and a hydraulic oil port, the first oil port of the reversing valve is connected to the hydraulic system oil inlet, the second oil port is connected to the hydraulic system oil return port, the third oil port is connected to the first hydraulic system oil output port, the fourth oil port is connected to the second hydraulic system oil output port, the double balance valve is connected in series between the third oil port and the first hydraulic system oil output port and between the fourth oil port and the second hydraulic system oil output port, and the two ends of the cartridge valve assembly are connected to the first hydraulic system oil output port and the second hydraulic system oil output port respectively. The compact steering gear special valve group has a smaller volume, a higher degree of product integration, and a smaller footprint.

Description

Technical Field

[0001] The invention relates to the technical field of ships, and in particular to a compact special valve group for a 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 hydraulic steering gears currently used on ships are mainly: swing cylinder type, fork type and rotary vane type. The swing cylinder type electric hydraulic steering gear uses a piston cylinder as an actuator to push the rudder tiller to rotate, thereby driving the rudder blade to rotate and realize the ship's steering. When the steering gear outputs a large torque, the stroke of the cylinder becomes very large, and the flow of the hydraulic system increases. If the valve is not selected and designed properly, the flow rate of the hydraulic system will be too high, the temperature of the hydraulic system will rise rapidly, and the pressure drop of the hydraulic oil after passing through the valve will be large. In severe cases, it will cause the steering gear to fail, resulting in ship control failure and ship collision. In addition, the existing valves have a low degree of integration, resulting in a large footprint.

[0004] Therefore, there is an urgent need for a compact special valve group for steering gear to solve the above problems. Summary of the invention

[0005] The object of the present invention is to provide a compact valve group dedicated to a steering gear, which has a higher degree of product integration and occupies a smaller area. When the rudder is subjected to a load, the torque of the rudder exceeds the set output torque of the steering gear, and the entire hydraulic system can be unloaded to prevent the entire hydraulic system from being overloaded, thereby protecting the entire hydraulic system.

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

[0007] A compact steering gear special valve group comprises a reversing valve, a double balancing valve, a cartridge valve assembly and a valve plate, wherein the reversing valve, the double balancing valve and the cartridge valve assembly are arranged on the valve plate, and a hydraulic system oil inlet, a hydraulic system oil return port, a first hydraulic system oil output port, a second hydraulic system oil output port and a hydraulic oil port are provided on the valve plate, the first oil port of the reversing valve is connected to the hydraulic system oil inlet, the second oil port of the reversing valve is connected to the hydraulic system oil return port, the third oil port of the reversing valve is connected to the first hydraulic system oil output port, the fourth oil port of the reversing valve is connected to the second hydraulic system oil output port, the double balancing valve is respectively connected in series between the third oil port and the first hydraulic system oil output port and between the fourth oil port and the second hydraulic system oil output port, and both ends of the cartridge valve assembly are respectively connected to the first hydraulic system oil output port and the second hydraulic system oil output port.

[0008] Preferably, the double balancing valve includes a first balancing valve and a second balancing valve connected to the first balancing valve, the first balancing valve and the second balancing valve are arranged on the valve plate, 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, which is arranged on the valve plate, 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 arranged on the valve plate, 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, the pressure relay is arranged on the valve plate, and the hydraulic reversing end of the reversing valve is connected to the hydraulic oil port.

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

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

[0016] Preferably, the valve plate is also provided with a first connecting oil port, a second connecting oil port, a third connecting oil port and a fourth connecting oil port, the third oil port is connected to the first connecting oil port and the second connecting oil port, and the first connecting oil port is connected in parallel with the second connecting oil port, the fourth oil port is connected to the third connecting oil port and the fourth connecting oil port, and the third connecting oil port is connected in parallel with the fourth connecting oil port.

[0017] Beneficial effects of the present invention:

[0018] The compact special valve group for steering gear provided by the present invention can effectively reduce the volume of the valve group by arranging the valve plate and the cartridge valve assembly, so as to make the product more integrated and occupy a smaller area. Moreover, when the rudder is subjected to extremely large external loads such as waves, currents and other floating objects, the torque of the rudder exceeds the set output torque of the steering gear, and the cartridge valve assembly works to unload the entire hydraulic system, thereby preventing the entire hydraulic system from being overloaded and protecting the entire hydraulic system. By arranging the reversing valve, the actuator of the entire hydraulic system can be reversed. The double balancing valve ensures that the reversing valve can be in a positive load pressure when the load is over-relaxed. Even if the load of the steering gear increases, the steering gear can still be stabilized at the set angle, thereby ensuring the rudder stability performance of the steering gear. 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 the description of 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 paying any creative work.

[0020] Figure 1 The structure of the compact steering gear valve group provided by the present invention is shown in FIG. Figure 1 ;

[0021] Figure 2 The structure of the compact steering gear valve group provided by the present invention is shown in FIG. Figure 2 ;

[0022] Figure 3 The present invention is a schematic diagram of the conduction connection principle of the compact special valve group for steering gear.

[0023] In the figure:

[0024] 100, reversing valve; 200, double 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, valve plate; 500, pressure relay; 600, high-pressure ball valve;

[0025] 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

[0026] The present invention will be further described in detail below in conjunction with the accompanying drawings and embodiments. It is to be understood that the specific embodiments described herein are only used to explain the present invention, rather than to limit the present invention. It should also be noted that, for ease of description, only parts related to the present invention, rather than all structures, are shown in the accompanying drawings.

[0027] In the description of the present invention, unless otherwise clearly specified and limited, the terms "connected", "connected", and "fixed" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0028] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0029] In the description of this embodiment, the terms "upper", "lower", "left", "right" and other directions or positional relationships are based on the directions or positional relationships shown in the drawings, and are only for the convenience of description and simplification of operation, rather than indicating or implying that the device or element referred to must have a specific direction, be constructed and operate in a specific direction, and therefore cannot be understood as limiting the present invention. In addition, the terms "first" and "second" are only used to distinguish in the description and have no special meaning.

[0030] like Figures 1 to 3 As shown, this embodiment provides a compact dedicated valve group for a steering gear, including a reversing valve 100, a double balancing valve 200, a cartridge valve assembly 300 and a valve plate 400. The reversing valve 100, the double balancing valve 200 and the cartridge valve assembly 300 are arranged 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 oil output port A1, a second hydraulic system oil output port B1 and a hydraulic oil port Y. 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.

[0031] The compact dedicated valve group for the steering gear provided in the present embodiment can effectively reduce the volume of the valve group by providing the valve plate 400 and the cartridge valve assembly 300, so as to make the product more integrated and occupy a smaller area. Moreover, when the rudder is subjected to extremely large external loads such as waves, currents and other floating objects, the torque of the rudder exceeds the set output torque of the steering gear, and the cartridge valve assembly 300 works to unload the entire hydraulic system, thereby preventing the entire hydraulic system from being overloaded and protecting the entire hydraulic system. By providing the reversing valve 100, the actuator of the entire hydraulic system can be reversed. The double balancing valve 200 ensures that the reversing valve 100 can be in a positive load pressure even when the load is over-relaxed. Even if the load of the steering gear increases, the steering gear can still be stabilized at the set angle, thereby ensuring the rudder stability performance of the steering gear.

[0032] The double balancing valve 200 in this embodiment includes a first balancing valve 201 and a second balancing valve 202, which are arranged on a valve plate 400, 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. By adopting the double balancing valve 200, it is ensured that the reversing valve 100 can be in a positive load pressure even when the load is over-relaxed. The working phenomenon of the steering gear is that even if the load of the steering gear increases, the steering gear can still be stable at the set angle, thereby improving the rudder stabilization performance of the steering gear. This embodiment adopts a double balancing valve 200 to replace the conventional hydraulic lock, thereby 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 rudder stabilization performance of the marine hydraulic steering gear.

[0033] As a preferred technical solution, the double balancing valve 200 can be but is not limited to a cartridge type. By adopting the cartridge type double balancing valve 200, the volume of the compact steering gear dedicated valve group 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.

[0034] The cartridge valve assembly 300 in this embodiment includes a first two-way cartridge valve 301, which is arranged on a valve plate 400, one oil port of the first two-way cartridge valve 301 is connected to the first hydraulic system output oil port A1, and the other oil port of the first two-way cartridge valve 301 is connected to the second hydraulic system output oil port B1. Through the above structure, the first two-way cartridge valve 301 can cooperate with the cover plate of the high-pressure overflow control function to form a safety valve. When the rudder is subjected to extremely large external loads such as waves, currents and other floating objects, the torque of the rudder exceeds the set output torque of the steering gear, and the first two-way cartridge valve 301 works to unload the entire hydraulic system, prevent the entire hydraulic system from being overloaded, and protect the entire hydraulic system.

[0035] Optionally, in a specific embodiment, the control chamber of the first two-way cartridge valve 301 is connected to the 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. Through the above structure, it is convenient to control the first two-way cartridge valve 301 and unload the entire hydraulic system; and after being connected to the hydraulic oil port Y, an external control type is formed, which can be unaffected by the hydraulic system. As a preferred technical solution, the other oil port of the first control valve group 302 is connected to one end of the first hydraulic system output oil port A1 close to the first balance valve 201 and one end of the second hydraulic system output oil port B1 close to the second balance valve 202. Through the above structure, an internal control type is formed, which is used in conjunction with the above external control type, and the control mode can be adjusted to the internal control type or the external control type as needed, and the adjustment is convenient.

[0036] In one embodiment, the cartridge valve assembly 300 further includes a second two-way cartridge valve 303, which is disposed on the valve plate 400, and is connected in parallel with the first two-way cartridge valve 301, and one oil port of the second two-way cartridge valve 303 is connected to the first hydraulic system output oil port A1, and the other oil port of the second two-way cartridge valve 303 is connected to the second hydraulic system output oil port B1. Through the above structure, the second two-way cartridge valve 303 can cooperate with the cover plate of the high-pressure overflow control function to form a safety valve. When the rudder is subjected to a particularly large external load such as waves, currents and other floating objects, the torque of the rudder exceeds the set output torque of the steering gear, and the first two-way cartridge valve 301 or the second two-way cartridge valve 303 works to unload the entire hydraulic system, prevent the entire hydraulic system from being overloaded, and protect the entire hydraulic system; and the first two-way cartridge valve 301 and the second two-way cartridge valve 303 are used in conjunction with each other, and the unloading effect of the hydraulic system is improved.

[0037] Optionally, in a specific embodiment, the control chamber of the second two-way cartridge valve 303 is connected to the 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. Through the above structure, it is convenient to control the second two-way cartridge valve 303 and unload the entire hydraulic system; and after being connected to the hydraulic oil port Y, it forms an external control type and is not affected by the hydraulic system. As a preferred technical solution, the other oil port of the second control valve group 304 is connected to one end of the first hydraulic system output oil port A1 close to the first balance valve 201 and one end of the second hydraulic system output oil port B1 close to the second balance valve 202. Through the above structure, an internal control type is formed, which is used in conjunction with the above external control type, and the control mode can be adjusted to the internal control type or the external control type as needed, and the adjustment is convenient.

[0038] The compact dedicated valve group for steering gear 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. Meanwhile, the first two-way cartridge valve 301 and the second two-way cartridge valve 303 are arranged on the valve plate 400, so that the volume of the compact dedicated valve group for steering gear is greatly reduced, the footprint of the electric hydraulic steering gear valve group is reduced, and the system has a high degree of integration.

[0039] 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 500, 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 actuator of the entire hydraulic system; by setting the pressure relay 500, the operation of the entire hydraulic system can be monitored, and when the pressure of the system is too low, an audible and visual alarm is issued.

[0040] 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, it is convenient to monitor the operation of the entire hydraulic system.

[0041] The compact steering gear dedicated valve group provided in this embodiment also includes a high-pressure ball valve 600, which is arranged on the valve plate 400, wherein one end of the high-pressure ball valve 600 is connected to the first hydraulic system output oil port A1, and the other end of the high-pressure ball valve 600 is connected to the second hydraulic system output oil port B1. By arranging the high-pressure ball valve 600 on the valve plate 400, the high-pressure ball valve 600 connects 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 circumstances. When the hydraulic system fails, the high-pressure ball valve 600 can be opened to connect the first hydraulic system output oil port A1 with the second hydraulic system output oil port B1, and the actuators connected to the first hydraulic system output oil port A1 and the second hydraulic system output oil port B1 are isolated.

[0042] The valve plate 400 in this embodiment is also provided with a first connecting oil port D1, a second connecting oil port D2, a third connecting oil port C1 and a fourth connecting oil port C2, wherein the first connecting oil port D1 and the second connecting oil port D2 are connected to the third oil port, and the first connecting oil port D1 and the second connecting oil port D2 are connected in parallel, and the third connecting oil port C1 and the fourth connecting oil port C2 are connected to the fourth oil port, and the third connecting oil port C1 and the fourth connecting oil port C2 are connected in parallel. Through the above structure, the hydraulic system of the steering gear is divided into two sets, and during use, a working mode of "one in use and one in reserve" is adopted. By setting the first connecting oil port D1 and the second connecting oil port D2 and the third connecting oil port C1 and the fourth connecting oil port C2, the two sets of hydraulic systems are connected in parallel. When a hydraulic system fails, the failed hydraulic system can be isolated through the first connecting oil port D1 and the second connecting oil port D2 and the third connecting oil port C1 and the fourth connecting oil port C2.

[0043] As a preferred technical solution, a working oil inlet A and a working oil return port B are also provided on the valve plate 400 , 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.

[0044] Obviously, the above 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. For those skilled in the art, various obvious changes, readjustments and substitutions can be made without departing from the protection scope of the present invention. It is not necessary and impossible to list all the embodiments here. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the claims of the present invention.

Claims

1. A compact valve group for steering gear, characterized in that: The invention comprises a reversing valve (100), a double balancing valve (200), a cartridge valve assembly (300) and a valve plate (400); the reversing valve (100), the double balancing valve (200) and the cartridge valve assembly (300) are arranged 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 oil output port A1, a second hydraulic system oil output port B1 and a hydraulic oil port Y; the first oil port of the reversing valve (100) is connected to the hydraulic system oil inlet P, and the second oil port of the reversing valve (100) is connected to the hydraulic system oil inlet The oil port 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 output oil port A1 of the first hydraulic system, the fourth oil port of the reversing valve (100) is connected to the output oil port B1 of the second hydraulic system, the double balancing valve (200) is respectively connected in series between the third oil port and the output oil port A1 of the first hydraulic system and between the fourth oil port and the output oil port B1 of the second hydraulic system, and the two ends of the cartridge valve assembly (300) are respectively connected to the output oil port A1 of the first hydraulic system and the output oil port B1 of the second hydraulic system; The double balancing valve (200) comprises a first balancing valve (201) and a second balancing valve (202) connected to the first balancing valve (201); the first balancing valve (201) and the second balancing valve (202) are arranged on the valve plate (400); 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), wherein the first two-way cartridge valve (301) is arranged on the valve plate (400), wherein one oil port of the first two-way cartridge valve (301) is connected to the first hydraulic system output oil port A1, and the other oil port of the first two-way cartridge valve (301) is 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 another oil port of the first control valve group (302) is connected to the hydraulic oil port Y; another oil port of the first control valve group (302) is also connected to one end of the first hydraulic system output oil port A1 close to the first balancing valve (201) and one end of the second hydraulic system output oil port B1 close to the second balancing valve (202); The cartridge valve assembly (300) further comprises a second two-way cartridge valve (303), wherein the second two-way cartridge valve (303) is arranged on the valve plate (400), the second two-way cartridge valve (303) is connected in parallel with the first two-way cartridge valve (301), one oil port of the second two-way cartridge valve (303) is connected to the first hydraulic system output oil port A1, and the other oil port of the second two-way cartridge valve (303) is 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; Another oil port of the second control valve group (304) is also connected to one end of the first hydraulic system oil output port A1 close to the first balancing valve (201) and one end of the second hydraulic system oil output port B1 close to the second balancing valve (202).

2. The compact steering gear dedicated valve group 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 (500); the pressure relay (500) is arranged on the valve plate (400); and the hydraulic reversing end of the reversing valve (100) is connected to the hydraulic oil port Y.

3. The compact steering gear dedicated valve group according to claim 2, characterized in that: The valve plate (400) is provided with a pressure measuring port X, and the electromagnetic reversing end of the reversing valve (100) is connected to the pressure measuring port X.

4. The compact dedicated valve group for steering gear according to claim 1, characterized in that: It also includes a high-pressure ball valve (600), which is arranged on the valve plate (400), one end of the high-pressure ball valve (600) is connected to the first hydraulic system oil output port A1, and the other end of the high-pressure ball valve (600) is connected to the second hydraulic system oil output port B1.

5. The compact dedicated valve group for steering gear according to claim 1, characterized in that: The valve plate (400) is also provided with a first connecting oil port D1, a second connecting oil port D2, a third connecting oil port C1 and a fourth connecting oil port C2. The third oil port is connected to the first connecting oil port D1 and the second connecting oil port D2, and the first connecting oil port D1 is connected in parallel with the second connecting oil port D2. The fourth oil port is connected to the third connecting oil port C1 and the fourth connecting oil port C2, and the third connecting oil port C1 is connected in parallel with the fourth connecting oil port C2.

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