Proportional reversing valve system integrated with load sensitive function

Abstract

The utility model relates to the technical field of reversing valves, and discloses a proportional reversing valve system integrated with a load sensitive function, which comprises a valve body, a proportional reversing valve core and a pressure compensation valve core, an oil outlet of the pressure compensation valve element is connected with an oil inlet of the proportional reversing valve element. The valve body is provided with a load pressure port which is connected with a working oil port of the proportional reversing valve element. A first cavity is arranged below the pressure compensation valve core, the first cavity is connected with the load pressure port, a spring is arranged in the first cavity, one end of the spring is connected with the pressure compensation valve core, and the other end of the spring is connected with the valve body; a control cavity is formed in the pressure compensation valve element and connected with an oil inlet of the pressure compensation valve element. According to the proportional reversing valve, the opening flow of the valve element of the proportional reversing valve can be stable, and the technical problem that in the prior art, flow output of a reversing valve is prone to being affected by external load changes is solved.

Description

Technical Field

[0001] This utility model relates to the field of directional valve technology, and in particular to a proportional directional valve system with integrated load-sensing function. Background Technology

[0002] In hydraulic systems, load-sensitive proportional directional valves are widely used in various mechanical equipment to control flow and direction, achieving efficient and stable hydraulic control. However, existing technologies still suffer from drawbacks in practical applications, such as the flow output being affected by changes in external load, as follows:

[0003] Chinese invention patent CN113639069B discloses a proportional directional valve with a main valve equipped with a displacement sensor and amplifier. Although it features a displacement sensor and feedback control, allowing the valve body position to be fed back to an external control system for a certain degree of precision control, the valve's flow output remains susceptible to changes in external load. That is, when the external load changes, the valve's flow output also changes accordingly, making it difficult to maintain a stable flow output. This will limit its application in scenarios requiring stable output, such as motion control in precision machinery. Utility Model Content

[0004] The present invention aims to at least solve the technical problem in the prior art that the flow output of the directional valve is easily affected by changes in external load.

[0005] Therefore, one objective of this utility model is to propose a proportional directional valve system with integrated load-sensing function, including a valve body, a proportional directional valve core, and a pressure compensation valve core.

[0006] Both the proportional directional valve core and the pressure compensation valve core are located inside the valve body; the oil inlet of the pressure compensation valve core is connected to the oil outlet of the oil tank; the oil outlet of the pressure compensation valve core is connected to the oil inlet of the proportional directional valve core.

[0007] The valve body is also provided with a load pressure port, which is connected to the working oil port of the proportional directional valve core; a first cavity is provided below the pressure compensation valve core, which is connected to the load pressure port, and a spring is provided in the first cavity, one end of which is connected to the pressure compensation valve core and the other end is connected to the valve body.

[0008] The pressure compensation valve core has a control chamber inside, and the control chamber is connected to the oil inlet of the pressure compensation valve core.

[0009] Furthermore, a damping port is provided below the control chamber, and the control chamber is connected to the oil inlet of the pressure compensation valve core through the damping port.

[0010] Furthermore, the valve core is provided with a valve port, which is slidably connected to the side wall of the oil inlet of the pressure compensation valve core.

[0011] Furthermore, a first boss is provided inside the valve body;

[0012] The first cavity is formed between the first boss and the bottom of the valve body, and the pressure compensation valve core is slidably connected to the first boss.

[0013] Furthermore, a second cavity is provided above the first cavity; the second cavity is provided with the oil outlet of the pressure compensation valve core, and the oil outlet of the pressure compensation valve core is connected to the oil inlet of the proportional directional valve core; the upper part of the second cavity is provided with the oil inlet of the pressure compensation valve core, and the pressure compensation valve core is slidably connected to the oil inlet of the pressure compensation valve core.

[0014] Furthermore, a second boss is provided on the valve body, and the oil inlet of the pressure compensation valve core is formed between the side walls of the second boss.

[0015] Furthermore, the valve body is provided with a third cavity, which is located above the second boss;

[0016] The third chamber is connected to the oil outlet of the oil tank, and the third chamber is connected to the second chamber through the pressure compensation valve core.

[0017] Furthermore, a third protrusion is provided on the valve body, the third protrusion is located above the third cavity, and the upper part of the compensation valve core is slidably connected to the third protrusion.

[0018] Furthermore, this also includes relief valves;

[0019] The oil inlet of the overflow valve is connected to the working oil port of the proportional directional valve, and the oil outlet of the overflow valve is connected to the oil inlet of the oil tank.

[0020] Furthermore, the system also includes a bus control module, a controller, and a position sensor;

[0021] The bus control module is connected to the proportional directional valve core via an oil circuit and is used to control the displacement of the proportional directional valve core; the controller is electrically connected to the bus control module; the position sensor is electrically connected to the controller; and the position sensor is connected to the proportional directional valve core.

[0022] The position sensor detects the position information of the proportional directional valve core and transmits it to the controller. The controller transmits the position signal to the remote control system. The remote control system compares the preset control target with the position information, generates an adjustment plan, and transmits it to the controller. The controller sends an adjustment signal to the bus control module according to the adjustment plan. The bus control module adjusts the position of the proportional directional valve core according to the adjustment signal.

[0023] This utility model discloses a proportional directional valve system with integrated load-sensing function, which has the following beneficial effects:

[0024] This invention, by setting a pressure compensation valve between the proportional directional valve core and the oil tank outlet, and connecting the load pressure port to the working oil port of the proportional directional valve core, allows the load pressure through the working oil port to be introduced into the pressure compensation valve. This pressure, along with a spring, pushes the compensation valve core to move, opening the oil inlet of the pressure compensation valve core and connecting the oil inlet, outlet, and first (or second) working oil port of the pressure compensation valve core. This invention utilizes the load pressure to adjust the oil pressure at the outlet of the pressure compensation valve core, ensuring that the pressure difference between the oil pressure at the inlet of the proportional directional valve core and the oil pressure at the working oil port of the proportional directional valve is constant (equal to the spring force). This stabilizes the flow rate of the proportional directional valve core, solving the technical problem in the prior art where the flow output of the directional valve is easily affected by changes in external load.

[0025] This invention features a proportional directional valve equipped with a manual control lever, enabling manual repositioning of the valve. To enhance control flexibility, the invention further includes a bus control module, a controller, and a position sensor. The position sensor transmits the detected valve core position information to the controller, which then transmits the position signal to a remote control system. The remote control system compares the preset control target with the position information, generates an adjustment scheme, and transmits it to the controller. The controller then sends an adjustment signal to the bus control module based on the adjustment scheme. The bus control module adjusts the valve core position of the proportional directional valve according to the adjustment signal, achieving high-precision automatic control.

[0026] This invention integrates manual and electronic control into a proportional directional valve system, allowing users to select the appropriate control mode according to their actual needs. It integrates electro-hydraulic proportional control and closed-loop feedback control system. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0028] Figure 1 This is a schematic diagram of a proportional directional valve system with integrated load-sensing function according to this utility model.

[0029] Figure 2 This is a schematic diagram of the pressure compensation valve structure of a proportional directional valve system with integrated load-sensing function according to this utility model;

[0030] Figure 3 This is a schematic diagram of the valve core of a pressure compensation valve in a proportional directional valve system with integrated load-sensing function according to this utility model.

[0031] Figure 4 This is a schematic diagram of the structure of a proportional directional valve system with integrated load-sensing function according to this utility model. Figure 1 ;

[0032] Figure 5 This is a schematic diagram of the structure of a proportional directional valve system with integrated load-sensing function according to this utility model. Figure 2 .

[0033] Figure label:

[0034] 1. Proportional directional valve core; 2. Pressure compensation valve core; 21. Damping port; 22. Valve body; 23. Control chamber; 24. Protrusion; 25. First boss; 26. Second boss; 27. Third boss; 28. Spring; 29. ​​Valve port; 3. Second relief valve; 4. First relief valve; 5. Manual operating mechanism; 6. Bus control module; 7. Controller. Detailed Implementation

[0035] Various embodiments and features of this utility model are described herein with reference to the accompanying drawings.

[0036] It should be understood that various modifications can be made to the embodiments described herein. Therefore, the above description should not be considered as limiting, but merely as an example of embodiments. Other modifications within the scope and spirit of this invention will be apparent to those skilled in the art.

[0037] The accompanying drawings, which are included in and form part of this specification, illustrate embodiments of the present invention and, together with the general description of the present invention given above and the detailed description of the embodiments given below, serve to explain the principles of the present invention.

[0038] These and other features of the present invention will become apparent from the following description of preferred forms of embodiments given as non-limiting examples, with reference to the accompanying drawings.

[0039] It should also be understood that although the present invention has been described with reference to some specific examples, those skilled in the art can certainly implement many other equivalent forms of the present invention, which have the features described in the claims and are therefore all within the scope of protection defined herein.

[0040] The above and other aspects, features and advantages of the present invention will become more apparent when taken in conjunction with the accompanying drawings and in view of the following detailed description.

[0041] Specific embodiments of the present invention will now be described with reference to the accompanying drawings; however, it should be understood that the claimed embodiments are merely examples of the present invention, which may be implemented in various ways. Well-known and / or repeated functions and structures have not been described in detail to avoid unnecessary or redundant details that could obscure the present invention. Therefore, the specific structural and functional details claimed herein are not intended to be limiting, but merely to serve as the basis and representative basis for the claims to teach those skilled in the art to use the present invention in a variety of substantially any suitable detailed structures.

[0042] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to 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 of this utility model.

[0043] In the description of this utility model, "first feature" and "second feature" may include one or more of the features.

[0044] In the description of this utility model, "multiple" means two or more.

[0045] In the description of this utility model, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or it may include the first and second features not being in direct contact but being in contact through another feature between them.

[0046] In the description of this utility model, the terms "above", "over" and "on top" for the first feature and the second feature include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.

[0047] In the description of this utility model, the terms "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this utility model. 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.

[0048] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

[0049] Figure 1 In this utility model, the A end and B end of the hydraulic motor or hydraulic cylinder refer to the connection ports of the two working chambers of the hydraulic motor or hydraulic cylinder, respectively.

[0050] Z and T are the oil supply port and oil outlet of the bus control module 6, respectively. The bus control module 6 includes a pilot valve for controlling the opening degree of the proportional directional valve core 1. This is existing technology and not the focus of this utility model, so it will not be described in detail here.

[0051] L1 is the pump end load pressure, which is the maximum pressure selected by the shuttle valve from the external load pressure Ls and the load pressure X at the A or B end of the hydraulic motor or hydraulic cylinder, and then introduced into the pump. This is existing technology and not the focus of this utility model, so it will not be described in detail here.

[0052] Example 1

[0053] like Figure 1 and Figure 2 As shown, this embodiment provides a proportional directional valve system with integrated load-sensing function, including valve body 22, proportional directional valve core 1 and pressure compensation valve core 2;

[0054] Both the proportional directional valve core 1 and the pressure compensation valve core 2 are disposed inside the valve body 22; the oil inlet Q of the pressure compensation valve core 2 is connected to the oil outlet P of the oil tank; the oil outlet of the pressure compensation valve core 2 is connected to the oil inlet P0 of the proportional directional valve core.

[0055] The valve body 22 is also provided with a load pressure port M, which is connected to the working oil port of the proportional reversing valve core; a first cavity is provided below the pressure compensation valve core, which is connected to the load pressure port M, and a spring 28 is provided in the first cavity. One end of the spring 28 is connected to the pressure compensation valve core 2, and the other end is connected to the valve body 22.

[0056] The pressure compensation valve core 2 has a control chamber 23 inside, and the control chamber 23 is connected to the oil inlet Q of the pressure compensation valve core 2.

[0057] When the working port of the proportional reversing valve core is closed, the control chamber 23 is filled with oil, which exerts a downward force on the compensation valve core, thereby closing the oil inlet of the compensation valve core 2.

[0058] When the working port of the proportional directional valve core is opened, the oil can enter the load pressure port M and the first chamber through the working port of the proportional directional valve core. The oil in the first chamber and the spring 28 can provide an upward force to the compensation valve core. When the upward force is greater than the downward force of the oil in the control chamber 23 on the compensation valve core 2, the compensation valve core 2 moves upward, opening the inlet Q of the compensation valve core 2. This adjusts the oil pressure at the outlet of the pressure compensation valve core, making the oil pressure difference between the inlet of the proportional directional valve core and the working port of the proportional directional valve a constant value (equal to the spring force). This stabilizes the flow rate of the proportional directional valve core and solves the technical problem in the prior art where the flow output of the directional valve is easily affected by changes in the external load.

[0059] Example 2

[0060] like Figure 1 and Figure 2 As shown, this embodiment provides a proportional directional valve system with integrated load-sensing function, including valve body 22, proportional directional valve core 1 and pressure compensation valve core 2;

[0061] Both the proportional directional valve core 1 and the pressure compensation valve core 2 are disposed inside the valve body 22; the oil inlet Q of the pressure compensation valve core 2 is connected to the oil outlet P of the oil tank; the oil outlet of the pressure compensation valve core 2 is connected to the oil inlet P0 of the proportional directional valve core.

[0062] The valve body 22 is also provided with a load pressure port M, which is connected to the working oil port of the proportional reversing valve core; a first cavity is provided below the pressure compensation valve core, which is connected to the load pressure port M, and a spring 28 is provided in the first cavity. One end of the spring 28 is connected to the pressure compensation valve core 2, and the other end is connected to the valve body 22.

[0063] The pressure compensation valve core 2 has a control chamber 23 inside, and the control chamber 23 is connected to the oil inlet Q of the pressure compensation valve core 2.

[0064] When the working port of the proportional reversing valve core is closed, the control chamber 23 is filled with oil, which exerts a downward force on the compensation valve core, thereby closing the oil inlet of the compensation valve core 2.

[0065] When the working port of the proportional directional valve core is opened, the oil can enter the load pressure port M and the first chamber through the working port of the proportional directional valve core. The oil in the first chamber and the spring 28 can provide an upward force to the compensation valve core. When the upward force is greater than the downward force of the oil in the control chamber 23 on the compensation valve core 2, the compensation valve core 2 moves upward, opening the inlet Q of the compensation valve core 2. This adjusts the oil pressure at the outlet of the pressure compensation valve core, making the oil pressure difference between the inlet of the proportional directional valve core and the working port of the proportional directional valve a constant value (equal to the spring force). This stabilizes the flow rate of the proportional directional valve core and solves the technical problem in the prior art where the flow output of the directional valve is easily affected by changes in the external load.

[0066] The difference between this embodiment and the first embodiment is that:

[0067] A damping port is provided below the control chamber 23, and the control chamber 23 is connected to the oil inlet Q of the pressure compensation valve core through the damping port.

[0068] like Figure 3 As shown, the pressure compensation valve core 2 is provided with a valve port 29, which is slidably connected to the side wall of the oil inlet Q of the pressure compensation valve core 2. The valve port 29 has a double U-shaped structure, which allows the pressure compensation valve core 2 to use different control algorithms in different flow ranges to ensure precise control under various flow requirements. Especially in the low flow range, the control prioritizes fine adjustments to ensure the accuracy and stability of the flow output.

[0069] The valve body 22 is provided with a first boss 25 inside;

[0070] The first cavity is formed between the first boss 25 and the bottom of the valve body 22, and the pressure compensation valve core 2 is slidably connected to the first boss 25.

[0071] A second cavity is provided above the first cavity; the second cavity is provided with the oil outlet N of the pressure compensation valve core 2, and the oil outlet N of the pressure compensation valve core is connected to the oil inlet Q of the proportional reversing valve core 2; the upper part of the second cavity is provided with the oil inlet Q of the pressure compensation valve core 2, and the pressure compensation valve core 2 is slidably connected to the oil inlet Q of the pressure compensation valve core 2.

[0072] The valve body 22 is provided with a second boss 26, and the oil inlet Q of the pressure compensation valve core is formed between the side walls of the second boss 26.

[0073] The valve body 22 is provided with a third cavity, which is located above the second boss 26;

[0074] The third chamber is connected to the oil outlet P of the oil tank, and the third chamber is connected to the second chamber through the pressure compensation valve core 2.

[0075] The valve body 22 is provided with a third protrusion 27, which is located above the third cavity. The upper part of the compensation valve core 2 is slidably connected to the third protrusion 27.

[0076] The pressure compensation valve core 2 is provided with a protrusion 24, and the valve port 29 is provided on the protrusion 24. The protrusion 24 is slidably connected to the second boss 26 to realize the opening and closing of the valve port 29. When the valve port 29 is open, the oil can enter the oil inlet Q of the pressure compensation valve core 2 through the oil tank outlet P, then enter the second cavity, and then enter the oil inlet P0 of the proportional reversing valve core 1, and then enter the hydraulic cylinder or hydraulic motor through the working oil port.

[0077] Example 3

[0078] like Figure 1 and Figure 2 As shown, this embodiment provides a proportional directional valve system with integrated load-sensing function, including valve body 22, proportional directional valve core 1 and pressure compensation valve core 2;

[0079] Both the proportional directional valve core 1 and the pressure compensation valve core 2 are disposed inside the valve body 22; the oil inlet Q of the pressure compensation valve core 2 is connected to the oil outlet P of the oil tank; the oil outlet of the pressure compensation valve core 2 is connected to the oil inlet P0 of the proportional directional valve core.

[0080] The valve body 22 is also provided with a load pressure port M, which is connected to the working oil port of the proportional reversing valve core; a first cavity is provided below the pressure compensation valve core, which is connected to the load pressure port M, and a spring 28 is provided in the first cavity. One end of the spring 28 is connected to the pressure compensation valve core 2, and the other end is connected to the valve body 22.

[0081] The pressure compensation valve core 2 has a control chamber 23 inside, and the control chamber 23 is connected to the oil inlet Q of the pressure compensation valve core 2.

[0082] When the working port of the proportional reversing valve core is closed, the control chamber 23 is filled with oil, which exerts a downward force on the compensation valve core, thereby closing the oil inlet of the compensation valve core 2.

[0083] When the working port of the proportional directional valve core is opened, the oil can enter the load pressure port M and the first chamber through the working port of the proportional directional valve core. The oil in the first chamber and the spring 28 can provide an upward force to the compensation valve core. When the upward force is greater than the downward force of the oil in the control chamber 23 on the compensation valve core 2, the compensation valve core 2 moves upward, opening the inlet Q of the compensation valve core 2. This adjusts the oil pressure at the outlet of the pressure compensation valve core, making the oil pressure difference between the inlet of the proportional directional valve core and the working port of the proportional directional valve a constant value (equal to the spring force). This stabilizes the flow rate of the proportional directional valve core and solves the technical problem in the prior art where the flow output of the directional valve is easily affected by changes in the external load.

[0084] A damping port is provided below the control chamber 23, and the control chamber 23 is connected to the oil inlet Q of the pressure compensation valve core through the damping port.

[0085] The pressure compensation valve core 2 is provided with a valve port 29, which is slidably connected to the side wall of the oil inlet Q of the pressure compensation valve core 2. The valve port 29 has a double U-shaped structure, which allows the pressure compensation valve core 2 to use different control algorithms in different flow ranges to ensure precise control under various flow requirements. Especially in the low flow range, the control prioritizes fine adjustments to ensure the accuracy and stability of the flow output.

[0086] The valve body 22 is provided with a first boss 25 inside;

[0087] The first cavity is formed between the first boss 25 and the bottom of the valve body 22, and the pressure compensation valve core 2 is slidably connected to the first boss 25.

[0088] A second cavity is provided above the first cavity; the second cavity is provided with the oil outlet N of the pressure compensation valve core 2, and the oil outlet N of the pressure compensation valve core is connected to the oil inlet Q of the proportional reversing valve core 2; the upper part of the second cavity is provided with the oil inlet Q of the pressure compensation valve core 2, and the pressure compensation valve core 2 is slidably connected to the oil inlet Q of the pressure compensation valve core 2.

[0089] The valve body 22 is provided with a second boss 26, and the oil inlet Q of the pressure compensation valve core is formed between the side walls of the second boss 26.

[0090] The valve body 22 is provided with a third cavity, which is located above the second boss 26;

[0091] The third chamber is connected to the oil outlet P of the oil tank, and the third chamber is connected to the second chamber through the pressure compensation valve core 2.

[0092] The valve body 22 is provided with a third protrusion 27, which is located above the third cavity. The upper part of the compensation valve core 2 is slidably connected to the third protrusion 27.

[0093] The pressure compensation valve core 2 is provided with a protrusion 24, and the valve port 29 is provided on the protrusion 24. The protrusion 24 is slidably connected to the second boss 26 to realize the opening and closing of the valve port 29. When the valve port 29 is open, the oil can enter the oil inlet Q of the pressure compensation valve core 2 through the oil tank outlet P, then enter the second cavity, and then enter the oil inlet P0 of the proportional reversing valve core 1, and then enter the hydraulic cylinder or hydraulic motor through the working oil port.

[0094] The difference between this embodiment and embodiments 1 and 2 is that:

[0095] It also includes an overflow valve; the oil inlet of the overflow valve is connected to the working oil port of the proportional directional valve, and the oil outlet of the overflow valve is connected to the oil inlet of the oil tank.

[0096] The overflow valve includes a first overflow valve 4 and a second overflow valve 3;

[0097] The proportional directional valve core 1 includes a first working port D and a second working port E.

[0098] The proportional directional valve core 1 includes a first working position a, a blocking position c, and a second working position b;

[0099] like Figure 1As shown, when the proportional directional valve core 1 is in the blocked position c, the A end and B end of the hydraulic motor or hydraulic cylinder are both connected to the oil inlet R of the oil tank. The oil outlet N of the pressure compensation valve core 2, the oil inlet of the first relief valve 4 and the second relief valve 3 are in the cut-off state. The oil outlets of the first relief valve 4 and the second relief valve 3 are both connected to the oil inlet R of the oil tank.

[0100] When the proportional directional valve core 1 is in the first working position a, the first working port D of the proportional directional valve core 1 is connected to the A end of the hydraulic motor or hydraulic cylinder through the first pipeline. The inlet Q of the pressure compensation valve core 2 is connected to the first working port D. The oil can sequentially enter the A end of the hydraulic motor or hydraulic cylinder through the inlet Q, outlet N, first working port D, and the first pipeline of the pressure compensation valve core 2. The B end of the hydraulic motor or hydraulic cylinder is connected to the oil tank inlet R. The oil can enter the oil tank inlet R from the B end of the hydraulic motor or hydraulic cylinder. The first relief valve 4 is connected to the first pipeline and controls the load pressure. The load pressure port M is connected to the first pipeline. The oil in the first pipeline enters the load pressure port M to adjust the oil pressure at the outlet of the pressure compensation valve core 2.

[0101] When the proportional directional valve core 1 is in the second working position b, the second working port E of the proportional directional valve core 1 is connected to the B end of the hydraulic motor or hydraulic cylinder through the second pipeline. The inlet port Q of the pressure compensation valve core 2 is connected to the second working port E. The oil can sequentially enter the B end of the hydraulic motor or hydraulic cylinder through the inlet port Q, outlet port N, second working port E, and second pipeline of the pressure compensation valve core 2. The A end of the hydraulic motor or hydraulic cylinder is connected to the oil tank inlet port R, and the oil can enter the oil tank inlet port R from the A end of the hydraulic motor or hydraulic cylinder. The inlet port of the second relief valve 3 is connected to the second pipeline, and the second relief valve 3 controls the load pressure. The load pressure port M is also connected to the second pipeline and is used to adjust the oil pressure at the outlet port of the pressure compensation valve core 2.

[0102] A valve plug is provided above the third protrusion 27, the head end of the pressure compensation valve core 2 abuts against the valve plug, and the valve plug is connected to the port of the valve body 22.

[0103] like Figure 2The diagram shows the state of the pressure compensation valve core 2 when the proportional directional valve core 1 is in the blocked position c and the oil tank is not supplying fluid. When the system starts supplying fluid, the oil enters the inlet Q of the pressure compensation valve core 2 from the oil tank outlet P through the valve port 29, and then enters the second chamber. The liquid in the second chamber enters the control chamber 23 through the damping port 21. The oil generates downward pressure in the control chamber 23, which pushes the pressure compensation valve core 2 to slide downward and compress the spring. When the valve port on the pressure compensation valve core 2 is closed by the second boss 27, the oil cannot enter the inlet Q of the pressure compensation valve core 2 through the valve port 29, and the pressure compensation valve core 2 and the spring 28 are in a balanced state.

[0104] When the proportional directional valve core 1 is in the first working position a, the oil in the first pipeline enters the first cavity through the load pressure port M, generating an upward thrust on the pressure compensation valve core 2, causing the pressure compensation valve core 2 to slide upward, thereby opening the valve port 29. The oil flows from the oil tank outlet P through the valve port 29 into the oil inlet Q of the pressure compensation valve core 2, then into the second cavity, and then through the valve core inlet P0 of the proportional directional valve core 1 into the first working oil port D, finally entering the A end of the hydraulic motor or hydraulic cylinder; or...

[0105] When the proportional directional valve core 1 is in the second working position b, the oil in the second pipeline enters the first cavity through the load pressure port M, generating an upward thrust on the pressure compensation valve core 2, causing the pressure compensation valve core 2 to slide upward, thereby opening the valve port 29. The oil flows from the oil tank outlet P through the valve port 29 into the oil inlet Q of the pressure compensation valve core 2, then into the second cavity, and then through the valve core inlet P0 of the proportional directional valve core 1 into the second working oil port E, finally entering the A end of the hydraulic motor or hydraulic cylinder; at this time, the control... The pressure at the valve inlet P0 of the proportional directional valve core 1 and the pressure in cavity 23 are the same, both equal to the sum of the spring force and the load pressure X. The pressure at the first working port D or the second working port E of the proportional directional valve core 1 is the load pressure. The difference between the pressure at the valve inlet P0 of the proportional directional valve core 1 and the pressure at the first working port D or the second working port E of the proportional directional valve core 1 is the spring force. The spring force is a fixed value. Therefore, the pressure compensation valve core 2 of this utility model can stabilize the opening flow of the valve core of the proportional directional valve core 1.

[0106] This invention utilizes load pressure to adjust the oil pressure at the outlet of the pressure compensation valve core, so that the oil pressure difference between the oil pressure at the inlet of the proportional directional valve core and the oil pressure at the working port of the proportional directional valve is a constant value (equal to the spring force), thereby stabilizing the flow rate at the opening of the proportional directional valve core and solving the technical problem in the prior art where the flow output of the directional valve is easily affected by changes in external load.

[0107] The proportional directional valve core 1 is equipped with a manual control lever 5 to realize the manual switching of the proportional directional valve core 1.

[0108] To enhance control flexibility, this invention integrates manual control and electro-hydraulic closed-loop control into a proportional directional valve system. Users can select the appropriate control mode according to their actual needs. By integrating electro-hydraulic proportional control and closed-loop feedback control system, high-precision automatic control can be achieved.

[0109] like Figure 4 As shown, specifically, this utility model also includes a controller 7 and a position sensor;

[0110] The bus control module 6 is connected to the proportional directional valve core 1 via an oil circuit and is used to control the displacement of the proportional directional valve core 1; the controller 7 is electrically connected to the bus control module 6; the position sensor is electrically connected to the controller 7; and the position sensor is connected to the proportional directional valve core.

[0111] The position sensor is connected to the proportional directional valve core 1. The position sensor transmits the position information of the proportional directional valve core 1 it detects to the controller 7. The controller 7 transmits the position signal to the remote control system. The remote control system compares the preset control target with the position information, generates an adjustment scheme, and transmits it to the controller 7. The controller sends an adjustment signal to the bus control module 6 according to the adjustment scheme. The bus control module adjusts the position of the proportional directional valve core 1 according to the adjustment signal.

[0112] like Figure 5 As shown, this utility model modularizes the proportional directional valve system with integrated load-sensing function. Each valve core is integrated into a single valve body, forming a module that can be independently maintained and replaced. This simplifies maintenance and improves system flexibility. Ports A, B, Z, T, L1, Ls, X, P, and R are located at the bottom of the module and are vertically installed. When maintenance or module replacement is required, only the module needs to be disassembled, avoiding system downtime and improving the efficiency and convenience of overall system maintenance.

[0113] Note that the above description is merely a preferred embodiment of the present invention and the technical principles employed. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein, and various obvious changes, readjustments, and substitutions can be made without departing from the scope of protection of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments, and may include many other equivalent embodiments without departing from the concept of the present invention. The scope of the present invention is determined by the scope of the appended claims.

Claims

1. A proportional directional valve system with integrated load-sensing function, characterized in that, This includes the valve body, the proportional directional valve core, and the pressure compensation valve core. Both the proportional directional valve core and the pressure compensation valve core are located inside the valve body; the oil inlet of the pressure compensation valve core is connected to the oil outlet of the oil tank; the oil outlet of the pressure compensation valve core is connected to the oil inlet of the proportional directional valve core. The valve body is also provided with a load pressure port, which is connected to the working oil port of the proportional directional valve core; a first cavity is provided below the pressure compensation valve core, which is connected to the load pressure port, and a spring is provided in the first cavity, one end of which is connected to the pressure compensation valve core and the other end is connected to the valve body. The pressure compensation valve core has a control chamber inside, and the control chamber is connected to the oil inlet of the pressure compensation valve core.

2. The proportional directional valve system with integrated load-sensing function according to claim 1, characterized in that, A damping port is provided below the control chamber, and the control chamber is connected to the oil inlet of the pressure compensation valve core through the damping port.

3. The proportional directional valve system with integrated load-sensing function according to claim 1, characterized in that, The pressure compensation valve core is provided with a valve port, which is slidably connected to the side wall of the oil inlet of the pressure compensation valve core.

4. The proportional directional valve system with integrated load-sensing function according to claim 3, characterized in that, The valve body is provided with a first protrusion inside; The first cavity is formed between the first boss and the bottom of the valve body, and the pressure compensation valve core is slidably connected to the first boss.

5. The proportional directional valve system with integrated load-sensing function according to claim 1, characterized in that, A second cavity is provided above the first cavity; the oil outlet of the pressure compensation valve core is provided on the second cavity; the oil inlet of the pressure compensation valve core is provided at the upper part of the second cavity, and the pressure compensation valve core is slidably connected to the oil inlet of the pressure compensation valve core.

6. The proportional directional valve system with integrated load-sensing function according to claim 5, characterized in that, The valve body is provided with a second boss, and the oil inlet of the pressure compensation valve core is formed between the side walls of the second boss.

7. The proportional directional valve system with integrated load-sensing function according to claim 6, characterized in that, The valve body is provided with a third cavity, which is located above the second boss; The third chamber is connected to the oil outlet of the oil tank, and the third chamber is connected to the second chamber through the pressure compensation valve core.

8. The proportional directional valve system with integrated load-sensing function according to claim 7, characterized in that, The valve body is provided with a third protrusion, which is located above the third cavity, and the upper part of the compensation valve core is slidably connected to the third protrusion.

9. The proportional directional valve system with integrated load-sensing function according to claim 1, characterized in that, It also includes an overflow valve; The oil inlet of the overflow valve is connected to the working oil port of the proportional directional valve, and the oil outlet of the overflow valve is connected to the oil inlet of the oil tank.

10. The proportional directional valve system with integrated load-sensing function according to claim 1, characterized in that, The system also includes a bus control module, a controller, and a position sensor; The bus control module is connected to the proportional directional valve core via an oil circuit and is used to control the displacement of the proportional directional valve core; the controller is electrically connected to the bus control module; the position sensor is electrically connected to the controller; and the position sensor is connected to the proportional directional valve core. The position sensor detects the position information of the proportional directional valve core and transmits it to the controller. The controller then transmits the position information to the remote control system. The remote control system compares the preset control target with the position information, generates an adjustment plan, and transmits it to the controller. The controller sends an adjustment signal to the bus control module according to the adjustment plan. The bus control module adjusts the position of the proportional directional valve core according to the adjustment signal.

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