Switching valve group, hydraulic control valve group and hydraulic system

Abstract

The invention relates to the technical field of hydraulic pressure, in particular to a switching valve bank, a hydraulic control valve bank and a hydraulic system. A switching valve group comprises at least two pressure oil ports, at least one valve body, at least one valve body, at least one valve body and at least one valve body, the oil supply path is correspondingly communicated with the pressure oil port; the switching valves are arranged corresponding to the pressure oil ports, pressure oil introduced by each pressure oil port flows to the corresponding oil supply way and the corresponding switching valve, and when the switching valves are located at the first position, the pressure oil ports are unloaded through the switching valves; when the switching valve is located at the second position, pressure oil introduced by the pressure oil port cannot pass through the switching valve; when the switching valve is located at the third position, the pressure oil port supplies oil to the standby accessory through the switching valve. The problems that in the prior art, due to the fact that an unloading channel of a hydraulic system of an excavator passes through all valve elements, accumulated pressure loss is large, and oil consumption in a standby state is increased are solved; and the service life of the hydraulic pump is greatly shortened due to the fact that the standby accessory can only be fixedly driven by the same hydraulic pump.

Description

Technical Field

[0001] This invention relates to the field of hydraulic technology, and in particular to a switching valve assembly, a hydraulic control valve assembly, and a hydraulic system. Background Technology

[0002] Open-center hydraulic control systems are widely used in mobile machines such as excavators. They typically employ two hydraulic pumps and an open-center multi-way valve, which generally has the following functions:

[0003] (1) Unloading function

[0004] When the mobile machine is in standby mode or during a gap in operation, the engine has a certain speed and the hydraulic pump has a certain displacement. At this time, there is still flow output, but no supply to the actuator. In order to avoid pressure buildup and overheating in the hydraulic system, there needs to be an unloading passage to drain this part of the flow back to the oil tank.

[0005] Therefore, the hydraulic fluid at the P port (connected to the hydraulic pump) of the open-center multi-way valve is divided into two paths: one path leads to the T port (connected to the oil tank), and the other path leads to the working port (connected to the hydraulic motor / cylinder). When no actuator is activated, the multi-way valve spool is in the neutral position, and all the hydraulic fluid flows from the pump into the T port through the spool, thus unloading the pump. When the actuator needs to operate, the multi-way valve spool begins to move under the pilot pressure, gradually reducing the proportion of hydraulic fluid flowing into the T port and gradually increasing the proportion flowing into the working port. This continues until the multi-way valve spool is completely reversed, at which point all the hydraulic fluid flows into the working port.

[0006] To achieve the above functions, open-center multi-way valve cores are generally of a three-position, six-way type. Each valve core needs to control the opening area connecting the P port to the T port and the P port to the working port. The valve core structure and valve body flow channel structure are relatively complex. Moreover, since this unloading passage passes through all valve cores, the cumulative pressure loss is large, increasing oil consumption in standby mode. In addition, since the opening area connecting the P port to the T port and the P port to the working port is controlled by the same valve core, it is impossible to flexibly control the proportion of hydraulic pump oil distributed to the T port and the working port, which limits the improvement of control performance.

[0007] (2) Straight-line walking function

[0008] For mobile machines like excavators with tracks on both sides, the open-center system typically uses two hydraulic pumps, each controlling a travel motor via two travel valve cores, to ensure that the tracks travel at roughly the same speed during dual-travel operations. However, if additional actions (boom, stick, bucket, swing, etc.) occur, one or two hydraulic pumps will need to allocate some flow to other actuators. This results in inconsistent flow distribution between the two travel motors, causing uneven track speeds and potentially leading to machine deviation or even tipping over.

[0009] To address this, a linear travel valve core is installed in the center multi-way valve. Under normal circumstances, the linear travel valve core is in the neutral position, and the two hydraulic pumps control the track movement and other actions on one side respectively. When the dual travel and loading actions are performed simultaneously, the flow distribution method of the two hydraulic pumps is changed by reversing the linear travel valve core: one hydraulic pump supplies two travel motors, and the other hydraulic pump supplies other actuators. Thus, each of the two travel motors receives half of the flow from one of the hydraulic pumps, and the tracks on both sides can maintain a basically the same travel speed.

[0010] The above methods solve the problem of misalignment during movement. However, multi-way valves require a linear movement valve core and complex flow channels to achieve linear movement, resulting in a more complex overall structure and larger overall size.

[0011] (3) Function of attachments

[0012] In addition to their normal operating devices, some mobile machines can be equipped with other working attachments, such as the hydraulic breaker for excavators. On existing open-center multi-way valves, the breaker's movement is typically controlled by a spare interlock valve core, supplied with oil by a hydraulic pump located on the side of the spare interlock valve core. Because the pressure impact during breaking operations is significant, it causes considerable damage to the hydraulic pump. Using the same hydraulic pump for the breaker's operation will drastically reduce its lifespan. Summary of the Invention

[0013] To address the technical problems in existing excavator hydraulic systems where the unloading path passes through all valve cores, resulting in significant cumulative pressure loss and increased oil consumption during standby, and where spare attachments can only be driven by the same hydraulic pump, leading to a substantial reduction in the pump's lifespan, this invention provides a switching valve group, a hydraulic control valve group, and a hydraulic system, thereby solving the aforementioned technical problems.

[0014] To solve the above-mentioned technical problems, the present invention provides a switching valve assembly, comprising:

[0015] There are at least two pressure oil ports, through which pressure oil is introduced;

[0016] The oil supply circuit is connected to the corresponding pressure oil port;

[0017] A switching valve is provided corresponding to the pressure port. The pressure oil introduced into each pressure port flows to the corresponding oil supply circuit and the corresponding switching valve. When the switching valve is in the first position, the pressure port is unloaded through the switching valve. When the switching valve is in the second position, the pressure oil introduced into the pressure port cannot pass through the switching valve. When the switching valve is in the third position, the pressure port supplies oil to the standby attachment through the switching valve.

[0018] According to one embodiment of the present invention, it further includes a confluence oil circuit, wherein the switching valve controls the pressure oil of the corresponding pressure port to enter the confluence oil circuit, and the confluence oil circuit supplies oil to the spare attachment.

[0019] According to one embodiment of the present invention, a selection valve is further provided between the confluence oil circuit and the standby attachment, and the selection valve controls the on / off connection between the confluence oil circuit and the standby attachment.

[0020] According to one embodiment of the present invention, the selector valve is a cone valve, the first port d of the selector valve is connected to the confluence oil circuit, the second port e of the selector valve is connected to the spare attachment, the selector valve has a spring cavity, and the pilot valve controls the opening and closing of the second port e to the spring cavity.

[0021] According to one embodiment of the present invention, the valve core of the selector valve integrates a one-way structure and a throttling structure, and the oil in the confluence oil path can flow to the spring cavity through the one-way structure and the throttling structure in the valve core.

[0022] According to one embodiment of the present invention, each pressure port is also connected to a safety oil circuit, wherein a safety valve is provided on the safety oil circuit.

[0023] The present invention also provides a hydraulic control valve assembly, comprising:

[0024] Switch valve group;

[0025] The working link is supplied with oil by the oil supply circuit.

[0026] According to one embodiment of the present invention, the working link includes a traveling link, which includes a left traveling link and a right traveling link. The left traveling link and the right traveling link are symmetrically arranged on both sides of the switching valve group, and the left traveling link and the right traveling link are respectively connected to different oil supply lines.

[0027] According to one embodiment of the present invention, the working link further includes several action links, and the oil supply circuit supplies oil to each action link through the oil distribution circuit. The oil distribution circuit is provided with a logic valve that controls the opening area of ​​the oil passage.

[0028] The present invention also provides a hydraulic system, comprising:

[0029] Pumps, at least two;

[0030] The hydraulic control valve group has each pressure port connected to a corresponding pump outlet.

[0031] The actuator is the one whose operation is controlled by the working link.

[0032] Based on the above technical solution, the technical effects that the present invention can achieve are as follows:

[0033] 1. The switching valve assembly of the present invention, by setting a switching valve with different working positions to control the direction of pressure oil, allows the pressure oil introduced into the corresponding pressure port to be directly unloaded through the switching valve without having to pass through several multi-way valve cores for unloading, resulting in low pressure loss and reduced oil consumption in standby mode. When the switching valve is in the second position, the pressure oil introduced into the corresponding pressure port cannot pass through the switching valve and only enters the oil supply circuit to drive the various actuators. When the switching valve is in the third position, the pressure oil introduced into the corresponding pressure port can be partially supplied to the spare attachment and partially supplied to the corresponding oil supply circuit. This can be achieved by controlling different switching positions. When the valve is in the third position, it switches the pressure oil introduced through different pressure ports to drive the standby attachment. This means switching different hydraulic pumps to supply oil to the standby attachment, which can effectively extend the life of the hydraulic pump. Each switching valve can control the pressure oil introduced through the corresponding pressure port to achieve three states: supplying oil only to the supply line, directly unloading, and supplying oil to both the supply line and the standby attachment. The hydraulic control valve group has at least two pressure ports and switching valves, which can introduce pressure oil from at least two points. By controlling the state of the corresponding switching valves, at least two pressure ports can alternately supply oil to the standby attachment, or at least two pressure ports can supply oil to the standby attachment together.

[0034] 2. The switching valve assembly of the present invention is equipped with a confluence oil circuit. When at least two switching valves are switched to the third position, the pressure oil introduced into the corresponding controlled pressure oil port can both enter the confluence oil circuit to achieve confluence. When straight-line travel is required, the pressure oil introduced into the two pressure oil ports corresponding to left and right travel can be controlled to enter the confluence oil circuit for confluence. In this way, the flow rate distributed to the two travel motors is the same, and the travel speed of the tracks on both sides is consistent, which can achieve straight-line travel without the need for a separate straight-line travel valve core, thus simplifying the structure.

[0035] 3. The switching valve assembly of the present invention is further provided with a selector valve, which controls the connection and disconnection between the confluence oil circuit and the standby attachment. When the standby attachment needs to be activated, the selector valve can be opened, allowing the pressure oil from the confluence oil circuit to enter the standby attachment and drive it to activate. When the standby attachment does not need to be activated, the selector valve can be closed, preventing the pressure oil from flowing to the standby attachment and serving only as a confluence valve. The selector valve is opened and closed under the control of a pilot valve. Specifically, the pilot valve is designed such that when the pilot valve is not subjected to pilot pressure, the pilot valve of the selector valve is in its initial state, i.e., the first working position, under the action of the spring. At this time, the connection between the second port of the selector valve and the spring cavity is broken. The oil from the confluence oil circuit enters the spring cavity through the one-way structure and throttling structure integrated in the valve core of the selector valve. The pressure in the spring cavity is basically the same as the pressure in the confluence oil circuit, and the valve core of the selector valve cannot be opened. When the pilot valve receives pilot pressure, it switches to the second working position, connecting the second port to the spring chamber. The oil in the confluence circuit enters the spring chamber through the one-way structure and throttling structure integrated in the valve core of the selector valve, and then enters the second port through the pilot valve. At this time, the pressure in the spring chamber is between the pressure in the confluence circuit and the pressure in the second port. Due to the effect of the throttling structure, the pressure in the spring chamber is closer to the pressure in the second port, so that the resultant force on the valve core of the selector valve can open it, allowing the oil in the confluence circuit to flow to the spare attachment.

[0036] 4. The hydraulic control valve group of the present invention includes a switching valve group and a working link. The left travel link and the right travel link of the working link are symmetrically arranged on both sides of the switching valve group. When straight travel is required, the two pressure oil ports can be connected to the merging oil circuit under the control of the switching valve to achieve merging. Then, oil is supplied to the left travel link and the right travel link through the oil supply circuit, so that the flow rate allocated to the left travel link and the right travel link is the same, thereby achieving straight travel.

[0037] 5. In the hydraulic control valve group of the present invention, each oil supply line also supplies oil to each action link through a branch oil line. The branch oil line is equipped with a logic valve that controls the opening area of ​​the oil passage, so that the flow rate of oil supplied by each oil supply line to each action link can be controlled.

[0038] 6. The hydraulic system of the present invention can realize independent unloading function, pump confluence function, and standby attachment switching and selection function by setting the switching valve group. The switching valve group can be integrated to simplify the structure and realize multi-functional switching. Attached Figure Description

[0039] Figure 1 This is a hydraulic schematic diagram of the switching valve assembly of the present invention;

[0040] Figure 2 This is a hydraulic schematic diagram of the hydraulic control valve assembly of the present invention;

[0041] Figure 3 The hydraulic schematic diagram for the left-hand drive linkage;

[0042] Figure 4 The hydraulic schematic diagram for the right-hand drive linkage;

[0043] Figure 5 This is a hydraulic schematic diagram of the boom linkage.

[0044] Figure 6 Hydraulic schematic diagram of the bucket assembly;

[0045] Figure 7 This is a hydraulic schematic diagram of the boom linkage.

[0046] Figure 8 The hydraulic schematic diagram for the rotary coupling;

[0047] In the picture:

[0048] 10-Switching valve assembly; 1-Fuel supply circuit; 11-First fuel supply circuit; 12-Second fuel supply circuit; 2-Switching valve; 21-First switching valve; 22-Second switching valve; 3-Combining circuit; 4-Selector valve; 41-Spring chamber; 42-One-way structure; 43-Throttle structure; 5-Pilot valve; 6-Safety circuit; 7-Safety valve; 81-First check valve; 82-Second check valve;

[0049] 201-Left travel linkage; 2011-Left travel main control valve; 2012-Left travel oil distribution circuit;

[0050] 202-Right travel linkage; 2021-Right travel main control valve; 2022-Right travel oil distribution circuit;

[0051] 301-Boom linkage; 3011-Boom main control valve; 3012-First oil distribution circuit; 3013-Second oil distribution circuit; 3014-First logic valve; 3015-Second logic valve; 3016-Boom holding valve; 3017-First pilot valve;

[0052] 302-Bucket linkage; 3021-Bucket main control valve; 3022-Third oil distribution circuit; 3023-Fourth oil distribution circuit; 3024-Third logic valve; 3025-Fourth logic valve;

[0053] 303-Hoist linkage; 3031-Hoist main control valve; 3032-Fifth oil circuit; 3033-Sixth oil circuit; 3034-Fifth logic valve; 3035-Sixth logic valve; 3036-Hoist holding valve; 3037-Second pilot valve; 3038-Hoist regeneration shut-off valve;

[0054] 304-Rotary coupling; 3041-Rotary main control valve; 3042-Seventh oil circuit; 3043-Seventh logic valve. Detailed Implementation

[0055] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0056] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0057] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps set forth in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it need not be further discussed in subsequent figures.

[0058] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0059] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0060] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0061] Example 1

[0062] like Figure 1 As shown, this embodiment proposes a switching valve assembly 10, including a pressure port, an oil supply line 1, and a switching valve 2. There are at least two pressure ports for introducing pressure oil; there are at least two oil supply lines 1, each corresponding to a pressure port P, allowing the pressure oil introduced through the pressure port to enter the corresponding oil supply line 1; there are also at least two switching valves 2, each corresponding to a pressure port, allowing the pressure oil introduced through the pressure port to flow to the corresponding oil supply line 1 and the switching valve 2, with the switching valve 2 controlling the direction of the pressure oil introduced through the corresponding pressure port. The switching valve 2 has a first position, a second position, and a third position. When the switching valve 2 is in the first position, the pressure port is unloaded via the switching valve 2, enabling direct unloading of the pressure port; when the switching valve 2 is in the second position, the pressure oil introduced through the pressure port cannot pass through the switching valve 2, and the pressure port only supplies oil to the corresponding oil supply line 1; when the switching valve 2 is in the third position, the pressure port can supply oil to a spare attachment via the switching valve 2.

[0063] The switching valve assembly 10 includes a valve body, the outer surface of which is provided with at least two pressure oil ports, and the inside of the valve body is provided with at least two oil supply lines 1 and at least two switching valves 2. Each pressure oil port is connected to one oil supply line 1 and one switching valve 2.

[0064] In this embodiment, two pressure ports are provided, namely pressure port P1 and pressure port P2; two corresponding oil supply lines 1 are provided, namely a first oil supply line 11 and a second oil supply line 12. Pressure port P1 is connected to the first oil supply line 11, and pressure port P2 is connected to the second oil supply line 12; two switching valves 2 are also provided, namely a first switching valve 21 and a second switching valve 22. Pressure port P1 is connected to the first switching valve 21, and pressure port P2 is connected to the second switching valve 22. The pressurized oil introduced by pressure port P1 can flow to the first oil supply line 11 and the first switching valve 21; the pressurized oil introduced by pressure port P2 can flow to the second oil supply line 12 and the second switching valve 22. Pressure ports P1 and P2 can be connected to the pump outlets of two pumps respectively.

[0065] The switching valve 2 can be a three-position three-way valve. The outer circumferential surface of the valve core of the switching valve 2 has three ports: one port connects to the corresponding pressure port, one port connects to the unloading port, and one port connects to the supply port of the standby attachment. When the switching valve 2 is in the first position, it controls the connection between the corresponding pressure port and the unloading port, allowing the pressure oil introduced through the pressure port to be directly unloaded. When the switching valve 2 is in the second position, none of the three ports are connected, and the pressure oil introduced through the pressure port is only supplied to the corresponding supply line 1, and cannot be supplied to the standby attachment. When the switching valve 2 is in the third position, it controls the connection between the corresponding pressure port and the supply port of the standby attachment, allowing the pressure oil introduced through the corresponding pressure port to be partially supplied to the corresponding supply line 1 and partially supplied to the standby attachment. By controlling different switching valves 2 to be in the third position, the pressure oil supplied to the standby attachment from different pressure ports can be switched.

[0066] In this embodiment, there are two switching valves 2, namely a first switching valve 21 and a second switching valve 22. The valve core of the first switching valve 21 has an oil port a1, an oil port b1 and an oil port c1 formed on its outer periphery. The oil port a1 is connected to the pressure oil port P1, the oil port b1 is connected to the unloading oil port R1, and the oil port c1 is connected to the oil supply port of the spare attachment. One end of the first switching valve 21 is provided with an elastic element, and the other end of the first switching valve 21 can be introduced with a pilot pressure XU1. In the initial state, the valve core of the first switching valve 21 can be in the first position under the action of the elastic element, so that oil port a1 and oil port b1 are connected. The pressure oil introduced by the pressure oil port P1 can flow through the first switching valve 21 to the unloading oil port R1 to achieve direct unloading. When a smaller pilot pressure XU1 is introduced, the valve core of the first switching valve 21 switches to the second position, so that oil ports a1, b1 and c1 are not connected. The pressure oil introduced by the pressure oil port P1 cannot pass through the first switching valve 21 and is only supplied to the first oil supply circuit 11. When a larger pilot pressure XU1 is introduced, the valve core of the first switching valve 21 switches to the third position, so that oil ports a1 and c1 are connected. The pressure oil introduced by the pressure oil port P1 can be supplied to the spare attachment through the first switching valve 21.

[0067] The valve core of the second switching valve 22 has oil ports a2, b2 and c2 on its outer periphery. Oil port a2 is connected to pressure oil port P2, oil port b2 is connected to unloading oil port R2, and oil port c2 is connected to the oil supply port of the spare attachment. One end of the second switching valve 22 is provided with an elastic element, and the other end of the second switching valve 22 can be introduced with a pilot pressure XU2. In the initial state, the valve core of the second switching valve 22 can be in the first position under the action of the elastic element, so that oil port a2 and oil port b2 are connected. The pressure oil introduced by the pressure oil port P2 can flow through the second switching valve 22 to the unloading oil port R2 to achieve direct unloading. When a smaller pilot pressure XU2 is introduced, the valve core of the second switching valve 22 switches to the second position, so that oil ports a2, b2 and c2 are not connected. The pressure oil introduced by the pressure oil port P2 cannot pass through the second switching valve 22 and is only supplied to the second oil supply circuit 12. When a larger pilot pressure XU2 is introduced, the valve core of the second switching valve 22 switches to the third position, so that oil ports a2 and c2 are connected. The pressure oil introduced by the pressure oil port P2 can be supplied to the spare attachment through the second switching valve 22.

[0068] The switching valve assembly 10 also includes a confluence oil passage 3. When the switching valve 2 is in the third position, the switching valve 2 can control the corresponding pressure port P to connect with the confluence oil passage 3, and the confluence oil passage 3 supplies oil to the standby attachment. Specifically, the oil port c of each switching valve 2 is connected to the confluence oil passage 3, and the confluence oil passage 3 can also serve to merge at least two pressure ports.

[0069] In this embodiment, the oil port c1 on the outer periphery of the valve core of the first switching valve 21 is connected to the confluence oil passage 3, and the oil port c2 on the outer periphery of the valve core of the second switching valve 22 is also connected to the confluence oil passage 3. When only the first switching valve 21 is in the third position, the pressurized oil introduced by the pressure port P1 enters the confluence oil passage 3 and then supplies oil to the standby attachment; when only the second switching valve 22 is in the third position, the pressurized oil introduced by the pressure port P2 enters the confluence oil passage 3 and then supplies oil to the standby attachment; when both the first switching valve 21 and the second switching valve 22 are in the third position, the pressurized oil introduced by both the pressure port P1 and the pressure port P2 enters the confluence oil passage 3 to achieve confluence, and oil can be supplied to the standby attachment.

[0070] The switching valve group 10 also includes a selection valve 4, which controls the connection and disconnection between the confluence oil circuit 3 and the standby attachment. When the selection valve 4 is closed, the pressure oil on the confluence oil circuit 3 cannot be supplied to the standby attachment; when the selection valve 4 is open, the pressure oil on the confluence oil circuit 3 can enter the standby attachment and drive the standby attachment to operate.

[0071] Specifically, the selector valve 4 can be configured as a cone valve. The selector valve 4 has a first port d and a second port e. The first port d is connected to the confluence oil passage 3, and the second port e is connected to the oil supply port Ao of the standby attachment. The selector valve 4 has a spring cavity 41. An elastic element acts on the valve core of the selector valve 4. Initially, under the action of the elastic element, the valve core of the selector valve 4 forms a seal, blocking the connection between the first port d and the second port e. When the pressure oil introduced into the confluence oil passage 3 exerts a force greater than the force exerted by the elastic element and the pressure inside the spring cavity 41, the valve core of the selector valve 4 overcomes the force of the elastic element and opens, connecting the first port d and the second port e. The pressure oil on the confluence oil passage 3 can then flow to the oil supply port Ao of the standby attachment, driving the standby attachment to operate.

[0072] As a preferred embodiment, the valve core of the selector valve 4 is further provided with a one-way structure 42 and a throttling structure 43. The oil entering through the first oil port d can enter the spring cavity 41 through the one-way structure 42 and the throttling structure 43. Specifically, an oil passage connecting the first oil port d and the spring cavity 41 can be provided in the valve core of the selector valve 4. The one-way structure 42 and the throttling structure 43 are provided on the oil passage. The one-way structure 42 can be a one-way valve, and the throttling structure 43 can be a damping orifice or a throttling plug.

[0073] As a preferred technical solution in this embodiment, the selector valve 4 is opened and closed under the control of the pilot valve 5. The pilot valve 5 controls the opening and closing of the second oil port e to the spring cavity 41. A spring is provided at one end of the pilot valve 5, and a pilot pressure Pno can be introduced at the other end of the pilot valve 5. When the pilot pressure Pno is not introduced, the valve core of the pilot valve 5 is in the initial state, i.e., the first working position, under the action of the spring. At this time, the connection between the second oil port e of the selector valve 4 and the spring cavity 41 is broken. The pressure oil on the confluence oil circuit 3 enters the spring cavity 41 through the one-way structure 42 and the throttling structure 43. Then the pressure in the spring cavity 41 is basically the same as the pressure on the confluence oil circuit 3, and the valve core of the selector valve 4 cannot be opened. When the pilot pressure Pno is introduced, the valve core of the pilot valve 5 overcomes the spring force and is in the second working position. At this time, the second port e of the selector valve 4 is connected to the spring cavity 41. The pressurized oil in the confluence oil circuit 3 enters the spring cavity 41 through the one-way structure 42 and the throttling structure 43, and then enters the second port e through the pilot valve 5. At this time, the oil pressure in the spring cavity 41 is between the oil pressure in the confluence oil circuit 3 and the oil pressure in the second port e. Due to the action of the throttling structure 43, the oil pressure in the spring cavity 41 is closer to the oil pressure in the second port e, so that the resultant force on the valve core of the selector valve 4 can open it, allowing the oil in the confluence oil circuit 3 to flow to the oil supply port Ao of the spare attachment. The selector valve 4 also has a load holding function, that is, when the oil pressure at the second port e of the selector valve 4 is higher than the oil pressure in the confluence oil circuit 3, the oil at the second port e will not flow back to the confluence oil circuit 3. The reasons are as follows: If the pilot valve 5 does not introduce pilot pressure Pno at this time, the passage of the pilot valve 5 is closed, and the oil at the second oil port e will flow into the spring chamber 41 from the side gap of the valve core of the selector valve 4, making the pressure of the spring chamber 41 the same as the pressure of the second oil port e, and the one-way structure 42 and the selector valve 4 cannot be opened; if the pilot valve 5 introduces pilot pressure Pno at this time, the second oil port e and the spring chamber 41 are directly connected through the pilot valve 5, and the pressure is the same, and the one-way structure 42 and the selector valve 4 also cannot be opened.

[0074] The switching valve assembly 10 also includes a safety oil circuit 6, on which a safety valve 7 is installed. Each pressure port is connected to the safety oil circuit 6 to ensure that the system pressure does not become too high. The safety valve 7 can be, but is not limited to, a relief valve.

[0075] In this embodiment, both pressure port P1 and pressure port P2 are connected to the safety oil circuit 6. A first check valve 81 is provided between pressure port P1 and the safety oil circuit 6, and a second check valve 82 is provided between pressure port P2 and the safety oil circuit 6. Since pressure port P1 and pressure port P2 are connected to the same safety oil circuit 6, the provision of the first check valve 81 and the second check valve 82 can ensure that the oil from pressure port P1 and pressure port P2 flows unidirectionally to the safety oil circuit 6, and will not flow in the opposite direction.

[0076] Based on the above technical solution, the switching valve group 10 of this embodiment can realize the direction control of the pressure oil introduced into at least two pressure oil ports, taking pressure oil port P1 and pressure oil port P2 as examples:

[0077] When the first switching valve 21 / second switching valve 22 is in the first position, the pressure oil introduced by the pressure oil port P1 / pressure oil port P2 can be directly unloaded. The pressure oil introduced by the pressure oil port only passes through one valve core, resulting in small pressure loss and reduced oil consumption in standby mode.

[0078] When the first switching valve 21 / second switching valve 22 is in the second position, the pressure oil introduced by the pressure oil port P1 / pressure oil port P2 can be controlled to be supplied only to the corresponding first oil supply line 11 / second oil supply line 12.

[0079] When the first switching valve 21 / second switching valve 22 is in the third position, the pressure oil introduced by the pressure oil port P1 / pressure oil port P2 can be controlled to supply oil to the corresponding first oil supply line 11 / second oil supply line 12 and confluence oil line 3.

[0080] When the selector valve 4 is closed, the pressurized oil in the confluence oil circuit 3 cannot enter the oil supply port Ao of the standby attachment; when the selector valve 4 is open, the pressurized oil in the confluence oil circuit 3 can enter the oil supply port Ao of the standby attachment.

[0081] Therefore, in standby mode, the pressure oil introduced by pressure oil port P1 / pressure oil port P2 can be directly unloaded by setting the first switching valve 21 / second switching valve 22 to the first position.

[0082] When the standby attachment does not need to be operated, the selector valve 4 can be controlled to be closed so that the pressure oil on the confluence oil circuit 3 cannot be supplied to the oil supply port Ao of the standby attachment. At this time, if the first switching valve 21 and the second switching valve 22 are both in the second position, the pressure oil port P1 supplies oil only to the first oil supply circuit 11, and the pressure oil port P2 supplies oil only to the second oil supply circuit 12. If the first switching valve 21 and the second switching valve 22 are both in the third position, the pressure oil from the pressure oil ports P1 and P2 can be combined through the confluence oil circuit 3, and the combined pressure oil from the pressure oil ports P1 and P2 supplies oil to the first oil supply circuit 11 and the second oil supply circuit 12.

[0083] When the backup attachment needs to be activated, the selector valve 4 can be controlled to be in the open state so that the pressure oil on the confluence oil circuit 3 can be supplied to the oil supply port Ao of the backup attachment; then the first switching valve 21 and / or the second switching valve 22 can be controlled to the third position. When the first switching valve 21 or the second switching valve 22 is in the third position, the pressure oil of the backup attachment can be switched; when both the first switching valve 21 and the second switching valve 22 are in the third position, the pressure oil introduced from the pressure oil ports P1 and P2 can be combined through the confluence oil circuit 3. The pressure oil from the pressure oil ports P1 and P2 is combined to supply oil to the backup attachment, and at the same time, it is combined to supply oil to the first oil supply circuit 11 and the second oil supply circuit 12.

[0084] Example 2

[0085] like Figure 2-8 As shown, this embodiment provides a hydraulic control valve group, including the switching valve group 10 of embodiment one, and also includes several working links, which are arranged on both sides of the switching valve group 10, and the oil supply circuit is supplied by the working links.

[0086] like Figure 2 As shown, the working link includes the traveling link, which includes the left traveling link 201 and the right traveling link 202. The left traveling link 201 and the right traveling link 202 are symmetrically arranged on both sides of the switching valve group 10. The left traveling link 201 and the right traveling link 202 are respectively connected to different oil supply lines.

[0087] As a preferred technical solution in this embodiment, such as Figure 3 As shown, the left-walking linkage 201 includes a left-walking main control valve 2011. The first oil supply line 11 supplies oil to the left-walking main control valve 2011 via the left-walking branch oil line 2012. The left-walking main control valve 2011 controls the oil inlet and outlet of the left-walking actuator. A one-way valve is installed on the left-walking branch oil line 2012 to allow the pressurized oil from the first oil supply line 11 to flow unidirectionally to the valve core of the left-walking control valve 2011. When no pilot pressure is applied to the left travel main control valve 2011, it is in the neutral position, and both working ports of the left travel actuator are connected to the oil tank, so the left travel actuator does not operate. When a pilot pressure XAtL is applied to the left travel main control valve 2011, it switches to the upper position. At this time, oil enters through port AtL and returns through port BtL, and the left travel mechanism drives the left track forward. When a pilot pressure XBtL is applied to the left travel main control valve 2011, it switches to the lower position. At this time, oil enters through port BtL and returns through port AtL, and the left travel mechanism drives the left track backward.

[0088] As a preferred technical solution in this embodiment, such as Figure 4As shown, the right-walk linkage 202 includes a right-walk main control valve 2021. The second oil supply line 12 supplies oil to the right-walk main control valve 2021 via the right-walk branch oil line 2022. The right-walk main control valve 2021 controls the oil inlet and outlet of the right-walk actuator. A check valve is installed on the right-walk branch oil line 2022 to allow the pressurized oil from the second oil supply line 12 to flow unidirectionally to the valve core of the right-walk control valve 2021. When the right travel main control valve 2021 is not subjected to pilot pressure, it is in the neutral position, and both working ports of the right travel actuator are connected to the oil tank, so the right travel actuator does not operate. When the right travel main control valve 2021 is subjected to pilot pressure XAtr, it switches to the upper position, at which point oil enters through port Atr and returns through port Btr, driving the right track forward. When the right travel main control valve 2021 is subjected to pilot pressure XBtr, it switches to the lower position, at which point oil enters through port Btr and returns through port Atr, driving the right track backward.

[0089] like Figure 2 As shown, the working link also includes several action links, including but not limited to the boom link 301, bucket link 302, stick link 303 and slewing link 304. These action links are arranged on both sides of the left travel link 201 and the right travel link 202 to control the corresponding actuator actions.

[0090] like Figure 5 As shown, the boom linkage 301 includes a boom main control valve 3011. The first oil supply line 11 and the second oil supply line 12 both supply oil to the boom main control valve 3011. The boom main control valve 3011 controls the oil inlet and outlet of the boom actuator.

[0091] As a preferred technical solution in this embodiment, specifically, the first oil supply line 11 supplies oil to the boom main control valve 3011 via the first branch oil line 3012, and the second oil supply line 12 supplies oil to the boom main control valve 3011 via the second branch oil line 3013. A first logic valve 3014 is provided on the first branch oil line 3012, which can control the opening area of ​​the first branch oil line 3012. A second logic valve 3015 is provided on the second branch oil line 3013, which can control the opening area of ​​the second branch oil line 3013. The first branch oil line 3012 and the second branch oil line 3013 converge before the valve core of the boom main control valve 3011. The opening areas of both the first logic valve 3014 and the second logic valve 3015 can be continuously adjusted between 0 and the maximum opening area. The opening areas of the first logic valve 3014 and the second logic valve 3015 can be adjusted by the pilot pressure Pnb1 and the pilot pressure Pnb2, respectively.

[0092] As a preferred technical solution in this embodiment, the first logic valve 3014 and the second logic valve 3015 also have a one-way valve function, which can play a role in load holding.

[0093] As a preferred embodiment, the boom linkage 301 further includes a boom holding valve 3016. The boom holding valve 3016 can be installed in the oil line from the boom main control valve 3011 to the boom large chamber Ab. A first pilot valve 3017 controls the connection between the control chamber of the boom holding valve 3016 and the boom large chamber Ab. When the boom main control valve 3011 is not subjected to pilot pressure, the boom main control valve 3011 is in the neutral position, and the boom actuator does not move. The first pilot valve 3017 can control the connection between the control chamber of the boom holding valve 3016 and the boom large chamber Ab. Under the action of the oil pressure in the control chamber, the valve core of the boom holding valve 3016 is in the closed state, which can prevent leakage between the boom large chamber Ab and the oil tank, so that the boom actuator will not automatically descend. When a pilot pressure XAb is applied to the boom control valve 3011, the valve core of the boom control valve 3011 switches to the upper position. At this time, oil enters the large chamber Ab of the boom and oil returns to the small chamber Bb, driving the boom lifting action. When a pilot pressure XBb is applied to the boom control valve 3011, the valve core of the boom control valve 3011 switches to the lower position. At the same time, a pilot pressure Pnb3 is applied to the first pilot valve 3017 to unlock the boom holding valve 3016. At this time, oil enters the small chamber Bb of the boom. Part of the oil in the large chamber Ab of the boom returns to the oil tank, and part of the oil returns to the small chamber Bb of the boom through the one-way valve inside the valve core of the boom control valve 3011, driving the boom lowering action and making full use of the gravitational potential energy during boom lowering to achieve energy saving.

[0094] As a preferred technical solution in this embodiment, the boom linkage 301 is also provided with a port overflow valve, which limits the pressure in the large chamber of the boom and the pressure in the small chamber of the boom to not exceed the set overflow pressure, thereby protecting the boom actuator.

[0095] like Figure 6 As shown, the bucket assembly 302 includes a bucket main control valve 3021. The first oil supply line 11 and the second oil supply line 12 both supply oil to the bucket main control valve 3021. The bucket main control valve 3021 controls the oil inlet and outlet of the bucket actuator.

[0096] As a preferred embodiment, the bucket main control valve 3021 can be configured as a three-position four-way valve. When no pilot pressure is applied to the bucket main control valve 3021, it is in the neutral position, and the bucket actuator does not move. When a pilot pressure XAk is applied to the bucket main control valve 3021, the valve core of the bucket main control valve 3021 switches to the upper position. At this time, oil enters the bucket small chamber Ak and oil returns to the bucket large chamber Bk, driving the bucket to swing outward. When a pilot pressure XBk is applied to the bucket main control valve 3021, the valve core of the bucket main control valve 3021 switches to the lower position. At this time, oil enters the bucket large chamber Bk and oil returns to the bucket small chamber Ak, driving the bucket to retract.

[0097] As a preferred technical solution of this embodiment, specifically, the first oil supply line 11 supplies oil to the bucket main control valve 3021 via the third branch oil line 3022, the second oil supply line 12 supplies oil to the bucket main control valve 3021 via the fourth branch oil line 3023, the third branch oil line 3022 is provided with a third logic valve 3024, which can control the opening area of ​​the third branch oil line 3022; the fourth branch oil line 3023 is provided with a fourth logic valve 3025, which can control the opening area of ​​the fourth branch oil line 3023. The third oil circuit 3022 and the fourth oil circuit 3023 converge in front of the valve core of the bucket main control valve 3021. The opening areas of the third logic valve 3024 and the fourth logic valve 3025 can be continuously adjusted between 0 and the maximum opening area. The opening areas of the third logic valve 3024 and the fourth logic valve 3025 can be adjusted by the pilot pressure Pnk1 and the pilot pressure Pnk2 respectively.

[0098] As a preferred technical solution in this embodiment, the third logic valve 3024 and the fourth logic valve 3025 also have a one-way valve function, which can play a role in load holding.

[0099] As a preferred technical solution in this embodiment, the bucket assembly 302 is also provided with a port overflow valve, which limits the pressure in the small chamber of the bucket and the pressure in the large chamber of the bucket to not exceed the set overflow pressure, thereby protecting the bucket actuator.

[0100] like Figure 7 As shown, the stick linkage 303 includes a stick main control valve 3031. The first oil supply line 11 and the second oil supply line 12 both supply oil to the stick main control valve 3031. The stick main control valve 3031 controls the oil inlet and outlet of the stick actuator.

[0101] As a preferred embodiment, the first oil supply line 11 supplies oil to the boom main control valve 3031 via the fifth branch oil line 3032, and the second oil supply line 12 supplies oil to the boom main control valve 3031 via the sixth branch oil line 3033. A fifth logic valve 3034 is installed on the fifth branch oil line 3032, which controls the opening area of ​​the fifth branch oil line 3032. A sixth logic valve 3035 is installed on the sixth branch oil line 3033, which controls the opening area of ​​the sixth branch oil line 3033. The fifth branch oil line 3032 and the sixth branch oil line 3033 converge before the valve core of the boom main control valve 3031. The opening areas of both the fifth logic valve 3034 and the sixth logic valve 3035 can be continuously adjusted between 0 and the maximum opening area. The opening areas of the fifth logic valve 3034 and the sixth logic valve 3035 can be adjusted by the pilot pressure Pna1 and the pilot pressure Pna2, respectively.

[0102] As a preferred technical solution in this embodiment, the fifth logic valve 3034 and the sixth logic valve 3035 also have a one-way valve function, which can play a role in load holding.

[0103] As a preferred embodiment, the boom linkage 303 further includes a boom holding valve 3036. The boom holding valve 3036 can be installed in the oil line from the boom main control valve 3031 to the boom small chamber Aa. The second pilot valve 3037 controls the connection between the control chamber of the boom holding valve 3036 and the boom small chamber Aa. When the boom main control valve 3031 is not subjected to pilot pressure, the boom main control valve 3031 is in the neutral position, and the boom actuator does not move. The second pilot valve 3037 can control the connection between the control chamber of the boom holding valve 3036 and the boom small chamber Aa. Under the action of the oil pressure in the control chamber, the valve core of the boom holding valve 3036 is in the closed state, which can prevent leakage between the boom small chamber Aa and the oil tank, so that the boom actuator will not descend automatically. When a pilot pressure XAa is applied to the boom main control valve 3031, the valve core of the boom main control valve 3031 switches to the upper position. At this time, oil enters the small chamber Aa of the boom and oil returns to the large chamber Ba of the boom, driving the boom to swing outward. When a pilot pressure XBa is applied to the boom main control valve 3031, the valve core of the boom main control valve 3031 switches to the lower position. At the same time, a pilot pressure Pna3 is applied to the second pilot valve 3037 to unlock the boom holding valve 3036. At this time, oil enters the large chamber Ba of the boom. Part of the oil in the small chamber Aa of the boom returns to the oil tank through the boom regeneration shut-off valve 3038, and part of the oil returns to the large chamber Ba of the boom through the one-way valve inside the valve core of the boom main control valve 3031, driving the boom to retract. The opening area of ​​the boom regeneration shut-off valve can be continuously adjusted between the minimum and maximum opening area under the pilot pressure Pna4. When the stick load pressure is low, a small pilot pressure Pna4 is applied, resulting in a small opening area for the stick regeneration shut-off valve. At this time, most of the oil in the stick's small chamber Aa returns to the stick's large chamber Ba through the check valve inside the valve core of the stick main control valve 3031, while a small portion returns to the oil tank through the stick regeneration shut-off valve. This utilizes the principle of a differential circuit to accelerate the stick's retraction speed. When the stick load pressure is high, a larger pilot pressure Pna4 is applied, resulting in a larger opening area for the stick regeneration shut-off valve. At this time, most of the oil in the stick's small chamber Aa returns to the oil tank through the stick regeneration shut-off valve, while a small portion returns to the stick's large chamber Ba through the check valve inside the valve core of the stick main control valve 3031, or all of it returns to the oil tank through the stick regeneration shut-off valve. This reduces the pressure in the stick's small chamber Aa and increases the stick's digging force.

[0104] As a preferred technical solution in this embodiment, the stick linkage 303 is also provided with a port overflow valve, which limits the pressure in the large chamber of the stick and the pressure in the small chamber of the stick to not exceed the set overflow pressure, thereby protecting the stick actuator.

[0105] like Figure 8 As shown, the rotary coupling 304 includes a rotary main control valve 3041, and the second oil supply line 12 supplies oil to the rotary main control valve 3041. The rotary main control valve 3041 controls the oil inlet and outlet of the rotary actuator.

[0106] As a preferred embodiment, the second oil supply line 12 supplies oil to the rotary main control valve 3041 via the seventh branch oil line 3042. A seventh logic valve 3043 is installed on the seventh branch oil line 3042, controlling the opening area of ​​the seventh branch oil line 3042. The opening area of ​​the seventh branch oil line 3043 can be continuously adjusted between 0 and the maximum opening area, and the opening area of ​​the seventh logic valve 3043 can be adjusted by the pilot pressure Pns.

[0107] As a preferred technical solution in this embodiment, the seventh logic valve 3043 also has a one-way valve function, which can play a role in load holding.

[0108] As a preferred embodiment, the rotary main control valve 3041 can be configured as a three-position four-way valve. When no pilot pressure is applied to the rotary main control valve 3041, it is in the neutral position, and the rotary actuator does not operate. When a pilot pressure XAs is applied to the rotary main control valve 3041, the valve core of the rotary main control valve 3041 switches to the upper position. At this time, oil enters through the rotary port As and returns through the rotary port Bs, and the rotary actuator drives the cockpit to turn left. When a pilot pressure XBs is applied to the rotary main control valve 3041, the valve core of the rotary main control valve 3041 switches to the lower position. At this time, oil enters through the rotary port Bs and returns through the rotary port As, and the rotary actuator drives the cockpit to turn right.

[0109] Multiple valve bodies can be stacked and fixed into a whole, which can provide hydraulic control for the various actuators of the excavator.

[0110] Example 3

[0111] This embodiment provides a hydraulic system, including a hydraulic control valve group as described in Embodiment 2, and also includes a pump and an actuator. There are at least two pumps, each pump is configured to connect to a pressure port, and the operation of the pump controls the corresponding actuator.

[0112] Specifically, when the pressure ports are set to include pressure port P1 and pressure port P2, two pumps are set accordingly, and the pump outlets of the two pumps are respectively connected to pressure port P1 and pressure port P2.

[0113] Specifically, the actuators may include a left travel actuator, a right travel actuator, a boom actuator, a bucket actuator, a stick actuator, and a swing actuator. The left travel main control valve 2011 controls the oil inlet and outlet of the left travel actuator, which drives the left track to travel; the right travel control valve 2021 controls the oil inlet and outlet of the right travel actuator, which drives the right track to travel; the boom main control valve 3011 controls the oil inlet and outlet of the boom actuator, which drives the boom to move; the bucket main control valve 3021 controls the oil inlet and outlet of the bucket actuator, which drives the bucket to move; the stick main control valve 3031 controls the oil inlet and outlet of the stick actuator, which drives the stick to move; and the swing main control valve 3041 controls the oil inlet and outlet of the swing actuator, which drives the cab to steer.

[0114] The hydraulic system also includes an actuator for a backup attachment. The backup attachment can be, but is not limited to, a breaker hammer. The actuator of the backup attachment is used to drive the backup attachment to move. The actuator of the backup attachment is connected to the oil supply port Ao of the backup attachment. When the backup attachment needs to move, the switching valve 2 can be switched to the third position to allow the pressure oil introduced by the corresponding pressure oil port to enter the confluence oil circuit 3. The selection valve 4 is also controlled to be open so that the oil in the confluence oil circuit 3 can enter the actuator of the backup attachment to drive the backup attachment to move.

[0115] The embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those skilled in the art, various changes can be made without departing from the spirit of the present invention.

Claims

1. A switching valve assembly, characterized in that, include: There are at least two pressure oil ports, through which pressure oil is introduced; The oil supply circuit (1) is connected to the pressure oil port. A switching valve (2) is set corresponding to a pressure port. The pressure oil introduced into each pressure port flows to the corresponding oil supply line (1) and the corresponding switching valve (2). When the switching valve (2) is in the first position, the pressure port is unloaded through the switching valve (2). When the switching valve (2) is in the second position, the pressure oil introduced into the pressure port cannot pass through the switching valve (2). When the switching valve (2) is in the third position, the pressure port supplies oil to the spare attachment through the switching valve (2).

2. A switching valve assembly according to claim 1, characterized in that, It also includes a merging oil circuit (3), wherein the switching valve (2) controls the pressure oil of the corresponding pressure port to enter the merging oil circuit (3), and the merging oil circuit (3) supplies oil to the spare attachment.

3. A switching valve assembly according to claim 2, characterized in that, A selection valve (4) is also provided between the combined oil circuit (3) and the standby attachment, and the selection valve (4) controls the opening and closing of the combined oil circuit (3) and the standby attachment.

4. A switching valve assembly according to claim 3, characterized in that, The selector valve (4) is a cone valve. The first port d of the selector valve (4) is connected to the confluence oil circuit (3), and the second port e of the selector valve (4) is connected to the spare attachment. The selector valve (4) has a spring cavity (41), and the pilot valve (5) controls the opening and closing of the second port e to the spring cavity (41).

5. A switching valve assembly according to claim 4, characterized in that, The valve core of the selector valve (4) integrates a one-way structure (42) and a throttling structure (43). The oil in the confluence oil circuit (3) can flow to the spring cavity (41) through the one-way structure (42) and the throttling structure (43) in the valve core.

6. A switching valve assembly according to claim 1, characterized in that, Each pressure port is also connected to a safety oil circuit (6), on which a safety valve (7) is provided.

7. A hydraulic control valve assembly, characterized in that, include: The switching valve assembly according to any one of claims 1-6; The working link, the oil supply line (1) supplies oil to the working link.

8. A hydraulic control valve assembly according to claim 7, characterized in that, The working link includes a traveling link, which includes a left traveling link (201) and a right traveling link (202). The left traveling link (201) and the right traveling link (202) are symmetrically arranged on both sides of the switching valve group. The left traveling link (201) and the right traveling link (202) are respectively connected to different oil supply lines (1).

9. A hydraulic control valve assembly according to claim 8, characterized in that, The working link also includes several action links. The oil supply line (1) supplies oil to each action link through the oil distribution line. The oil distribution line is equipped with a logic valve that controls the opening area of ​​the oil passage.

10. A hydraulic system, characterized in that, include: Pumps, at least two; The hydraulic control valve assembly according to any one of claims 7-9, wherein each pressure port is connected to a corresponding pump outlet; The actuator is the one whose operation is controlled by the working link.

Images