Hydraulic control one-way integrated reversing valve, lower control hydraulic module and operation machine
By setting a throttling channel in the hydraulically controlled one-way integrated directional valve, the problem of hydraulic shock during the switching process of the hydraulically controlled one-way valve is solved, and the smooth operation and reliability of the hydraulic system are improved.
Patent Information
- Application Number
- CN202520332818.7
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-02-27
- Publication Date
- 2026-02-10
- Estimated Expiration
- 2035-02-27
AI Technical Summary
Existing hydraulically controlled check valves lack a delayed closing function during the switching process, causing the hydraulically controlled check valve to be subjected to large hydraulic shocks, which affects the stability of the hydraulic system.
A hydraulically controlled one-way integrated directional valve was designed. By setting a throttling channel between the valve core and the valve chamber, the delayed closing function of the hydraulically controlled one-way valve is realized, thus avoiding hydraulic shock.
It effectively avoids the hydraulic shock problem caused by the sudden reversing of the directional valve, increases the smoothness of the hydraulic system operation, reduces the probability of blockage of the throttling channel, and improves the reliability of the hydraulically controlled one-way integrated directional valve.
Smart Images
Figure CN223894595U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The utility model belongs to engineering machinery technical field, concretely relates to a kind of hydraulic control one-way integrated reversing valve, lower portion control hydraulic module and operating machine. BACKGROUND
[0002] In hydraulic system, to simplify hydraulic pipeline layout, multiple reversing valves are usually integrated together to form integrated valve. In some cases, to realize the reversing control of execution unit (such as oil cylinder) and hydraulic lock function, some integrated valves integrate hydraulic control one-way valve and reversing valve together to form hydraulic control one-way integrated reversing valve.
[0003] For example, patent CN216742251U discloses the principle of hydraulic control one-way integrated reversing valve, as shown in Figure 1 When the reversing valve 011 in the hydraulic control one-way integrated reversing valve is in the lower valve position, the first pressure oil port 014 of the reversing valve 011 is connected with the pressure oil path P, so that the pilot oil port of the hydraulic control one-way valve 012 is high pressure, and the reverse conduction function of the hydraulic control one-way valve 012 is opened. However, when the reversing valve 011 is suddenly switched from the lower valve position to the middle position, the first pressure oil port 014 is immediately connected with the return oil passage T, and the reverse conduction function of the hydraulic control one-way valve 012 is immediately closed, resulting in that the hydraulic control one-way valve 012 will bear a large hydraulic impact. UTILITY MODEL CONTENTS
[0004] In view of the above defects or deficiencies, the utility model provides a hydraulic control one-way integrated reversing valve, a lower portion control hydraulic module and an operating machine, aiming to solve the technical problem of lack of delay closing function of the hydraulic control one-way valve in the existing hydraulic control one-way integrated reversing valve.
[0005] To achieve the above purpose, the utility model provides a hydraulic control one-way integrated reversing valve, wherein the hydraulic control one-way integrated reversing valve includes a reversing valve unit and a hydraulic control one-way valve unit. The reversing valve unit includes a first valve body part and a first valve core. The first valve body part is provided with an axially penetrating first valve cavity. The valve wall of the first valve body part is further provided with a first oil inlet, a first working oil port and a first return oil port, which are respectively connected with the first valve cavity. The first valve core is arranged in the first valve cavity and is provided with a cutoff valve position and a first working valve position when the first working oil port is under pressure. At the cutoff valve position, a throttling groove is formed between the first valve core and the inner wall of the first valve cavity, which connects the first return oil port and the first working oil port. The hydraulic control one-way valve unit is arranged side by side with the reversing valve unit and is provided with a hydraulic control pilot oil port for controlling reverse conduction. The hydraulic control pilot oil port is connected with the first working oil port.
[0006] In an embodiment of this utility model, the first return port and the first working port are arranged adjacent to each other. The first valve cavity includes a first valve cavity portion between the first working port and the first return port. The first valve core includes a first protrusion for blocking the first valve cavity portion in the shut-off valve position and a first guide groove disposed adjacent to the first protrusion and aligned with the first working port. The outer peripheral wall of the first protrusion is also provided with a throttling channel communicating with the first guide groove. In the first working valve position, the inner wall of the first valve cavity portion shields the throttling channel. In the shut-off valve position, the throttling channel is at least partially aligned with the first return port.
[0007] In embodiments of this utility model, the cross-sectional area of the throttling channel is set between 0.3 and 1.2 mm².
[0008] In an embodiment of this utility model, there are multiple throttling channels along the circumferential direction of the first valve core.
[0009] In an embodiment of this utility model, the first oil inlet is adjacent to the first working oil port and spaced apart from the first return oil port. The first valve chamber further includes a second valve chamber portion located between the first working oil port and the first oil inlet. The first valve core includes a second protrusion for blocking the second valve chamber portion in the shut-off valve position and a second guide groove disposed adjacent to the second protrusion and aligned with the first oil inlet. The second guide groove and the first guide groove are separated by the second protrusion. In the shut-off valve position, the inner wall of the second valve chamber portion shields the second protrusion. In the first working valve position, the second protrusion is offset from the inner wall of the second valve chamber portion, and the second guide groove connects the first oil inlet and the first working oil port.
[0010] In an embodiment of this utility model, the first valve body is further provided with a second working oil port, and the first valve core is further provided with a second working valve position of the second working oil port. In the second working valve position, the first oil inlet supplies oil to the second working oil port, and the first working oil port is connected to the first oil return port.
[0011] In an embodiment of this utility model, the hydraulic control check valve is provided with a forward connection port, a reverse connection port, and a hydraulic control pilot port. The forward connection port is connected to the second working port, the hydraulic control pilot port is connected to the first working port, the reverse connection port is used to connect to one of the working ports of the execution unit, and the first working port is used to connect to the other working port of the execution unit.
[0012] In an embodiment of this utility model, the hydraulic control check valve includes a second valve body, a second valve core, a plug, and an elastic reset member. The second valve body has an axially extending second valve cavity. One end of the second valve cavity is a pilot control end, and the other end is a reset end. The hydraulic pilot port is located near the pilot control end. The plug is located on the reset end and is aligned with the reverse connection port. The second valve core passes through from the pilot control end toward the reset end. The second valve core also has a pilot working groove aligned with the hydraulic pilot port. The reset member is located on the side of the plug facing away from the second valve core.
[0013] When the plug body compresses the elastic reset member toward the reset end, the reverse connection port will be misaligned with the plug body and connected to the forward connection port.
[0014] To achieve the above objectives, this utility model also provides a lower control hydraulic module, wherein the lower control hydraulic module includes a hydraulically controlled one-way integrated directional valve, a leg drive cylinder, a main inlet oil circuit, and a main return oil circuit as described above. One working chamber of the leg drive cylinder is connected to the first working port of the hydraulically controlled one-way integrated directional valve, and the other working chamber of the leg drive cylinder is connected to the reverse connection port of the hydraulically controlled one-way valve; the main inlet oil circuit and the main return oil circuit are respectively connected to the first inlet oil port and the first return oil port of the hydraulically controlled one-way integrated directional valve.
[0015] To achieve the above objectives, this utility model also provides a working machine, wherein the working machine includes a lower control hydraulic module as described above.
[0016] Through the above technical solution, the hydraulically controlled one-way integrated directional valve provided in this utility model embodiment has the following beneficial effects:
[0017] In the first working valve position, the pressure oil from the first inlet flows through the first working port to one of the ports of the actuator. Since the first working port is high-pressure oil, the pilot port of the hydraulic control check valve is also high-pressure. The reverse conduction function of the hydraulic control check valve is activated, and the hydraulic lock function of the hydraulic control check valve is released. The hydraulic oil from the other port of the actuator can return through the hydraulic control check valve.
[0018] When the directional valve suddenly switches from the first working valve position to the shut-off valve position (neutral position), the first working port will be throttled and connected to the first return port through the throttling channel. Therefore, the hydraulic oil between the pilot hydraulic port and the first working port can be depressurized to the first return port through the throttling channel, thereby closing the reverse connection function of the pilot hydraulic check valve and opening the hydraulic lock function.
[0019] The hydraulically controlled check valve of this invention exhibits a closing delay during the reverse conduction function closing process (i.e., the throttling effect of the throttling channel causes the hydraulic pilot port to fully depressurize in tens of milliseconds). This effectively avoids hydraulic shock problems in the actuator caused by sudden reversing of the directional valve linkage, increasing the smoothness of the hydraulic system operation. Furthermore, the throttling channel in this invention is formed between the inner wall of the first valve core and the first valve chamber. Since the first valve core is a moving part, even if foreign objects enter the throttling channel, the first valve core can squeeze and push them out during reversing, effectively reducing the probability of blockage in the throttling channel and increasing the reliability of the hydraulically controlled check valve.
[0020] Other features and advantages of this invention will be described in detail in the following detailed description section. Attached Figure Description
[0021] The accompanying drawings are provided to illustrate the present invention and form part of the specification. They are used together with the following detailed description to explain the present invention, but do not constitute a limitation thereof. In the drawings:
[0022] Figure 1 It is based on the schematic diagram of the hydraulically controlled one-way integrated directional valve in the background technology;
[0023] Figure 2 This is a schematic diagram of the internal structure of the reversing valve assembly when it is in the shut-off valve position according to an embodiment of the present utility model;
[0024] Figure 3 This is a schematic diagram of the internal structure of the reversing valve when it is in the first working valve position according to the embodiment of this utility model;
[0025] Figure 4 This is a schematic diagram of the structural principle of the hydraulic control check valve assembly according to the embodiments of this utility model;
[0026] Figure 5 This is a schematic diagram of the principle of the hydraulically controlled one-way integrated directional valve according to the embodiments of this utility model;
[0027] Figure 6 This is a hydraulic schematic diagram of the hydraulic control module according to an embodiment of the present utility model.
[0028] Explanation of reference numerals in the attached figures
[0029] 1. Reversing valve connection; 11. First valve body; 11P, First oil inlet; 11A, First working oil port; 11T, First return oil port; 11C, Throttling channel; 11B, Second working oil port; 11z, First valve cavity; 11x, Second valve cavity; 12. First valve core; 121, First protrusion; 121a, First guide groove; 122, Second protrusion; 122a, Second guide groove; 2. Hydraulic control check valve connection; 21. Second valve body; 21A, Forward connection oil port; 21B, Reverse connection oil port; 21C, Hydraulic control pilot oil port; 22. Second valve core; 221, Pilot working groove; 23. Plug; 24. Elastic reset element; 2A, Pilot control end; 2B, Reset end; 31. Outrigger drive cylinder; 32. Secondary reversing connection; 33. Main oil inlet circuit; 34. Main return oil circuit. Detailed Implementation
[0030] The specific embodiments of this utility model will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for illustration and explanation only and are not intended to limit the scope of this utility model.
[0031] The hydraulically controlled one-way integrated directional valve of this utility model is described below with reference to the accompanying drawings.
[0032] This utility model provides a hydraulically controlled one-way integrated directional valve, wherein, as shown in the figure... Figure 2 , Figure 4 and Figure 5 As shown, the hydraulically controlled one-way integrated directional valve includes a directional valve assembly 1 and a hydraulically controlled one-way valve assembly 2.
[0033] The reversing valve assembly 1 includes a first valve body 11 and a first valve core 12. The first valve body 11 has an axially penetrating first valve chamber. The valve wall of the first valve body 11 is also provided with a first oil inlet 11P, a first working oil port 11A and a first return oil port 11T that are respectively connected to the first valve chamber. The first valve core 12 is inserted into the first valve chamber and has a shut-off valve position and a first working valve position when the first working oil port 11A is pressurized oil. In the shut-off valve position, a throttling channel 11C is formed between the first valve core 12 and the inner wall of the first valve chamber, which connects the first return oil port 11T and the first working oil port 11A.
[0034] The hydraulic control check valve 2 and the reversing valve 1 are arranged side by side and are provided with a hydraulic control pilot port 21C for controlling reverse conduction. The hydraulic control pilot port 21C is connected to the first working port 11A.
[0035] like Figure 3 and Figure 5 As shown, in the first working valve position ( Figure 5(In the upper position of the middle position), the pressure oil of the first inlet 11P will flow to one of the ports of the actuator through the first working port 11A. Since the first working port 11A is high pressure oil, the hydraulic pilot port 21C of the hydraulic control check valve 2 is high pressure. The reverse conduction function of the hydraulic control check valve 2 is opened, the hydraulic lock function of the hydraulic control check valve 2 is released, and the hydraulic oil of the other port of the actuator can return through the hydraulic control check valve 2.
[0036] like Figure 2 and Figure 5 As shown, the directional valve 1 abruptly switches from the first working valve position to the shut-off valve position. Figure 5 When the first working port 11A is in the middle position, it will be throttled and connected to the first return port 11T through the throttling channel 11C. Therefore, the hydraulic oil between the hydraulic pilot port 21C and the first working port 11A can be depressurized to the first return port 11T through the throttling channel 11C, thereby closing the reverse connection function of the hydraulic control check valve 2 and opening the hydraulic lock function.
[0037] In summary, the hydraulically controlled check valve of this invention exhibits a closing delay during the reverse conduction function closing process (i.e., the throttling effect of the throttling channel 11C causes the hydraulically controlled pilot port 21C to take tens of milliseconds to fully depressurize). This effectively avoids the hydraulic shock problem of the actuator caused by the sudden reversing of the directional valve link 1, increasing the stability of the hydraulic system operation. Furthermore, the throttling channel 11C in this invention is formed between the first valve core 12 and the inner wall of the first valve chamber. Since the first valve core 12 is a moving part, even if foreign objects enter the throttling channel 11C, the first valve core 12 can squeeze and push the foreign objects out during reversing, thereby effectively reducing the probability of blockage in the throttling channel 11C and increasing the reliability of the hydraulically controlled check valve.
[0038] like Figure 2 and Figure 3 As shown, in an embodiment of this utility model, the first return port 11T can be arranged adjacent to the first working port 11A. The first valve chamber includes a first valve chamber portion 11z located between the first working port 11A and the first return port 11T. The first valve core 12 includes a first protrusion 121 for blocking the first valve chamber portion 11z in the shut-off valve position and a first guiding groove 121a disposed adjacent to the first protrusion 121 and aligned with the first working port 11A. The outer peripheral wall of the first protrusion 121 is also provided with a throttling channel 11C communicating with the first guiding groove 121a. In the first working valve position, the inner wall of the first valve chamber portion 11z shields the throttling channel 11C. In the shut-off valve position, the throttling channel 11C is at least partially aligned with the first return port 11T.
[0039] When the directional valve assembly 1 is in the first working valve position, the first protrusion 121 blocks the first valve cavity 11z, and the inner wall of the first valve cavity 11z shields the throttling channel 11C. At this time, the connection between the first working port 11A and the first return port 11T is cut off. When the directional valve assembly 1 is in the shut-off valve position, the axial end of the throttling channel 11C away from the first guide groove 121a will be connected to the first return port 11T. At this time, the hydraulic oil in the first working port 11A can enter the first return port 11T in sequence through the first guide groove 121a and the throttling channel 11C, thereby realizing the pressure relief of the first working port 11A and the hydraulic pilot port 21C.
[0040] In embodiments of this invention, the cross-section of the throttling channel 11C can be of various shapes, such as rectangular, triangular, or polygonal. Taking a rectangular or U-shaped channel as an example, the width of the throttling channel 11C can be 2-4 mm, the axial extension length of the throttling channel 11C can be 3-4 mm, and the depth of the throttling channel 11C can be 0.15-0.3 mm. This allows the throttling channel 11C to achieve both superior anti-clogging capability and throttling performance.
[0041] Furthermore, when changing the cross-sectional shape of the throttling channel 11C, it is preferable to set the cross-sectional area of the throttling channel 11C to 0.3-1.2 mm. 2 Between these ranges, the cross-sectional area of the U-shaped groove, as exemplified above, falls within this range.
[0042] In the embodiments of this utility model, the number of throttling channels 11C along the circumferential direction of the first valve core 12 can be multiple, such as two throttling channels 11C. The two throttling channels 11C are symmetrically arranged along the circumferential direction. The symmetrical design can ensure that the valve core is subjected to uniform force around its circumference and avoid abnormal wear of the valve core due to uneven force.
[0043] like Figure 2 and Figure 3 As shown, in an embodiment of this utility model, the first oil inlet 11P is adjacent to the first working oil inlet 11A and spaced apart from the first return oil inlet 11T. The first valve chamber also includes a second valve chamber portion 11x located between the first working oil inlet 11A and the first oil inlet 11P. The first valve core 12 includes a second protrusion 122 for blocking the second valve chamber portion 11x in the shut-off valve position and a second guiding groove 122a disposed adjacent to the second protrusion 122 and aligned with the first oil inlet 11P. The second guiding groove 122a and the first guiding groove 121a are separated by the second protrusion 122. In the shut-off valve position, the inner wall of the second valve chamber portion 11x covers the second protrusion 122. In the first working valve position, the second protrusion 122 is offset from the inner wall of the second valve chamber portion 11x, and the second guiding groove 122a connects the first oil inlet 11P and the first working oil inlet 11A.
[0044] The first oil inlet 11P is used to connect to the pressure oil circuit of the hydraulic system. When the directional valve 1 is in the first working valve position, the second guide groove 122a will connect the first oil inlet 11P to the first working oil port 11A, and the pressure oil in the first oil inlet 11P will enter the first working oil port 11A. The reverse conduction function of the hydraulic pilot check valve 2 is activated. When the directional valve 1 is in the shut-off valve position, the second protrusion 122 will block the second valve chamber 11x, and the connection between the first oil inlet 11P and the first working oil port 11A will be cut off. At the same time, the axial end of the throttling channel 11C away from the first guide groove 121a will be connected to the first return oil port 11T. The hydraulic oil in the first working oil port 11A can enter the first return oil port 11T in sequence through the first guide groove 121a and the throttling channel 11C, thereby realizing the pressure relief of the first working oil port 11A and the hydraulic pilot port 21C.
[0045] like Figure 2 , Figure 3 and Figure 5 As shown in the embodiment of this utility model, the first valve body 11 is further provided with a second working oil port 11B, and the first valve core 12 is further provided with a second working valve position of the second working oil port 11B. In the second working valve position, the first oil inlet 11P supplies oil to the second working oil port 11B, and the first working oil port 11A is connected to the first oil return port 11T.
[0046] Specifically, such as Figure 4 and Figure 5 As shown, the hydraulically controlled check valve assembly 2 includes a forward connection port 21A, a reverse connection port 21B, and a hydraulically controlled pilot port 21C. When the hydraulically controlled pilot port 21C is at low pressure, the hydraulically controlled check valve assembly 2 is configured to open when hydraulic oil flows from the forward connection port 21A to the reverse connection port 21B and close in the reverse direction. The forward connection port 21A is used to communicate with the second working port 11B, the hydraulically controlled pilot port 21C is used to communicate with the first working port 11A, the reverse connection port 21B is used to connect externally to one of the working ports of the actuator unit, and the first working port 11A is used to connect externally to the other working port of the actuator unit.
[0047] In the first working position, the pressure oil from the first working port 11A flows to one of the ports of the actuator, and the reverse conduction function of the hydraulic check valve 2 is activated. The hydraulic oil from the other port of the actuator returns through the reverse connection port 21B, the forward connection port 21A, and the second working port 11B in sequence. In the second working position, the pressure oil from the second working port 11B enters the corresponding port of the actuator through the forward connection port 21A and the reverse connection port 21B in sequence. The other port of the actuator returns through the first working port 11A.
[0048] In the embodiments of this utility model, the specific structural form of the hydraulically controlled check valve 2 can be many, such as... Figure 4 As shown, the hydraulically controlled one-way valve assembly 2 may include a second valve body 21, a second valve core 22, a plug 23, and an elastic reset member 24. The second valve body 21 has an axially extending second valve chamber. One end of the second valve chamber is a pilot control end 2A, and the other end is a reset end 2B. The hydraulically controlled pilot port 21C is located near the pilot control end 2A. The plug 23 is located on the reset end 2B and is aligned with the reverse connection port 21B. The second valve core 22 passes through from the pilot control end 2A toward the reset end 2B. The second valve core 22 also has a pilot working groove 221 aligned with the hydraulically controlled pilot port 21C. The reset member is located on the side of the plug 23 facing away from the second valve core 22. When the plug 23 compresses the elastic reset member 24 toward the reset end 2B, the reverse connection port 21B will be misaligned with the plug 23 and connected to the forward connection port 21A. When high-pressure oil enters the hydraulic pilot port 21C, it will push the second valve core 22 towards the plug body 23. The plug body 23 will be displaced, and the reverse connection port 21B will connect with the forward connection port 21A.
[0049] It is understandable that, for example Figure 2 As shown, in the first valve body 11, there can be multiple first oil inlets 11P and first oil return ports 11T. Multiple first oil inlets 11P or multiple first oil return ports 11T can be connected inside the valve body or outside the valve body through pipelines.
[0050] like Figure 6 As shown, to achieve the above objectives, this utility model also provides a lower control hydraulic module, wherein the lower control hydraulic module includes a hydraulically controlled one-way integrated directional valve, a leg drive cylinder 31, a main inlet oil circuit 33, and a main return oil circuit 34 as described above. One working chamber of the leg drive cylinder 31 is connected to the first working port 11A of the hydraulically controlled one-way integrated directional valve, and the other working chamber of the leg drive cylinder 31 is connected to the reverse connection port 21B of the hydraulically controlled one-way valve 2. A secondary directional valve 32 can be provided between the leg drive cylinder 31 and the first working port 11A, and / or between the leg drive cylinder 31 and the second working port 11B. The main inlet oil circuit 33 and the main return oil circuit 34 are respectively connected to the first inlet port 11P and the first return port 11T of the hydraulically controlled one-way integrated directional valve.
[0051] The hydraulically controlled one-way integrated directional valve of this invention can be applied to the lower control hydraulic module to realize the extension and retraction control of the side outriggers and the fifth outrigger of the working machinery. Of course, the hydraulically controlled one-way integrated directional valve of this invention can also be applied to other hydraulic modules with hydraulic lock functions.
[0052] To achieve the above objectives, this utility model also provides a working machine, wherein the working machine includes a lower control hydraulic module as described above. Since the working machine adopts all the technical solutions of the above embodiments, it at least has the beneficial effects brought about by the above embodiments, and will not be repeated here.
[0053] In the description of this utility model, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.
[0054] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.
[0055] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.
[0056] Although embodiments of the present invention have been described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.
Claims
1. A hydraulically controlled one-way integrated directional valve, characterized in that, The hydraulically controlled one-way integrated directional valve includes: The reversing valve assembly (1) includes a first valve body (11) and a first valve core (12). The first valve body (11) has an axially penetrating first valve chamber. The valve wall of the first valve body (11) is also provided with a first oil inlet (11P), a first working oil port (11A) and a first return oil port (11T) respectively connected to the first valve chamber. The first valve core (12) is inserted into the first valve chamber and has a shut-off valve position and a first working valve position when the first working oil port (11A) is pressurized oil. When the shut-off valve position is in the shut-off valve position, a throttling channel (11C) connecting the first return oil port (11T) and the first working oil port (11A) is formed between the first valve core (12) and the inner wall of the first valve chamber. A hydraulic control check valve (2) is arranged side by side with the reversing valve (1) and is provided with a hydraulic control pilot port (21C) for controlling reverse flow. The hydraulic control pilot port (21C) is connected to the first working port (11A).
2. The hydraulically controlled one-way integrated directional valve according to claim 1, characterized in that, The first return port (11T) is arranged adjacent to the first working port (11A). The first valve chamber includes a first valve chamber portion (11z) between the first working port (11A) and the first return port (11T). The first valve core (12) includes a first protrusion (121) for blocking the first valve chamber portion (11z) at the shut-off valve position and a first guide groove (121a) disposed adjacent to the first protrusion (121) and aligned with the first working port (11A). The outer peripheral wall of the first protrusion (121) is also provided with the throttling channel (11C) communicating with the first guide groove (121a). In the first working valve position, the inner wall of the first valve cavity (11z) shields the throttling channel (11C), and in the shut-off valve position, the throttling channel (11C) is at least partially located opposite the first return port (11T).
3. The hydraulically controlled one-way integrated directional valve according to claim 2, characterized in that, The cross-sectional area of the throttling channel (11C) is between 0.3 and 1.2 mm². 2 between.
4. The hydraulically controlled one-way integrated directional valve according to claim 2, characterized in that, Along the circumferential direction of the first valve core (12), there are multiple throttling channels (11C).
5. The hydraulically controlled one-way integrated directional valve according to claim 2, characterized in that, The first oil inlet (11P) is adjacent to the first working oil port (11A) and spaced apart from the first oil return port (11T). The first valve chamber also includes a second valve chamber portion (11x) between the first working oil port (11A) and the first oil inlet (11P). The first valve core (12) includes a second protrusion (122) for blocking the second valve chamber portion (11x) at the shut-off valve position and a second guide groove (122a) disposed adjacent to the second protrusion (122) and aligned with the first oil inlet (11P). The second guide groove (122a) and the first guide groove (121a) are separated by the second protrusion (122). In the shut-off valve position, the inner wall of the second valve cavity (11x) covers the second protrusion (122). In the first working valve position, the second protrusion (122) is offset from the inner wall of the second valve cavity (11x), and the second guide groove (122a) connects the first oil inlet (11P) and the first working oil port (11A).
6. The hydraulically controlled one-way integrated directional valve according to any one of claims 1 to 5, characterized in that, The first valve body (11) is also provided with a second working oil port (11B), and the first valve core (12) is also provided with a second working valve position of the second working oil port (11B). In the second working valve position, the first oil inlet (11P) supplies oil to the second working oil port (11B), and the first working oil port (11A) is connected to the first oil return port (11T).
7. The hydraulically controlled one-way integrated directional valve according to claim 6, characterized in that, The hydraulic control check valve assembly (2) is provided with a forward connection port (21A), a reverse connection port (21B), and a hydraulic control pilot port (21C). The forward connection port (21A) is connected to the second working port (11B), and the hydraulic control pilot port (21C) is connected to the first working port (11A). The reverse connection port (21B) is used to connect to one of the working ports of the execution unit, and the first working port (11A) is used to connect to the other working port of the execution unit.
8. The hydraulically controlled one-way integrated directional valve according to claim 7, characterized in that, The hydraulic control check valve (2) includes a second valve body (21), a second valve core (22), a plug (23), and an elastic reset member (24). The second valve body (21) has an axially extending second valve chamber. One end of the second valve chamber is a pilot control end (2A), and the other end is a reset end (2B). The hydraulic pilot port (21C) is located close to the pilot control end (2A). The plug (23) is located on the reset end (2B) and is positioned opposite the reverse connection port (21B). The second valve core (22) passes through from the pilot control end (2A) toward the reset end (2B). The second valve core (22) also has a pilot working groove (221) aligned with the hydraulic pilot port (21C). The reset member is located on the side of the plug (23) facing away from the second valve core (22). When the plug (23) compresses the elastic reset member (24) toward the reset end (2B), the reverse connection port (21B) will be misaligned with the plug (23) and connected to the forward connection port (21A) through the second valve chamber.
9. A lower control hydraulic module, characterized in that, The lower control hydraulic module includes: The hydraulically controlled one-way integrated directional valve according to any one of claims 1 to 8; Outrigger drive cylinder (31), one of the working chambers of the outrigger drive cylinder (31) is connected to the first working port (11A) in the hydraulic control one-way integrated directional valve, and the other working chamber of the outrigger drive cylinder (31) is connected to the reverse connection port (21B) of the hydraulic control one-way valve (2). The main oil inlet (33) and the main oil return (34) are respectively connected to the first oil inlet (11P) and the first oil return (11T) in the hydraulically controlled one-way integrated directional valve.
10. A type of operating machinery, characterized in that, Includes the lower control hydraulic module as described in claim 9.