Dual throttle valve control module and hydraulic system

Abstract

A dual throttle valve control module and a hydraulic system. The dual throttle valve control module comprises: a valve body (1), provided with a plurality of oil ports; throttle valve assemblies (2), wherein two throttle valve assemblies (2) are provided, the throttle valve assemblies (2) are symmetrically arranged in the valve body (1), each throttle valve assembly (2) comprises a valve core (21), and the valve cores (21) block the communication between the oil ports under the action of elastic members (22); and a driving member (3), located between the two throttle valve assemblies (2), gaps are provided between two ends of the driving member (3) and the two valve cores (21), respectively, and the driving member (3) pushes the valve core (21) on one side to open so as to control the opening degree. The hydraulic system comprises: a hydraulic cylinder (5); and the dual throttle valve control module, wherein one of the throttle valve assemblies (2) controls the hydraulic cylinder (5) to rise, and the other of the throttle valve assemblies (2) controls the hydraulic cylinder (5) to lower.

Description

A dual throttle valve control module and hydraulic system Technical Field

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

[0002] In hydraulic systems, 2-position 2-way throttle valves are commonly used control elements to control the on / off state between two ports and the flow area at the valve orifice. However, when controlling the motion of actuators such as lifting hydraulic cylinders, two or more 2-position 2-way throttle valves are often required. Common solutions include using multiple plate-type 2-position 2-way throttle valves or installing multiple 2-position 2-way throttle valve inserts on an integrated valve assembly. This means that regardless of whether the throttle valve is manually or electromagnet-driven, the entire control system requires multiple drive devices, resulting in significant space requirements and higher costs.

[0003] Another way to control multiple valve ports with fewer drive devices is through multi-position multi-way directional valves (such as two-position three-way or three-position four-way directional valves). However, this type of directional valve uses a single valve core to control the opening and closing of multiple oil ports, and all valve ports are linked and coupled, lacking the function of independently controlling the area of ​​multiple valve ports. Summary of the Invention

[0004] To address the technical problems in existing technologies where each throttle valve requires a corresponding drive device, resulting in large space requirements, or where shared drive devices cause interlocking between throttle valves, making independent control impossible, this invention provides a dual throttle valve control module and hydraulic system, solving the aforementioned technical problems.

[0005] To solve the above-mentioned technical problems, the present invention provides a dual throttle valve control module, comprising:

[0006] The valve body has multiple oil ports.

[0007] The throttle valve assembly consists of two sets symmetrically arranged within the valve body. Each throttle valve assembly includes a valve core, which, under the action of an elastic element, forms abutment to block the communication between oil ports.

[0008] A drive unit is located between two sets of throttle valve assemblies. The two ends of the drive unit are respectively separated from the two valve cores. The drive unit pushes a single valve core to open to control the opening degree.

[0009] According to one embodiment of the present invention, a through hole is formed in the valve core to connect the two ends, a flow groove is formed on the drive member, and the cavity between the valve core and the drive member is connected to the oil return port through the flow groove.

[0010] According to one embodiment of the present invention, the middle part of the drive member is reduced in size and connected to the oil return port, and the two ends of the drive member form the flow grooves, which extend from the end face of the drive member to the middle part of the drive member.

[0011] According to one embodiment of the present invention, the flow channel includes a radial channel located on the end face of the drive member and an axial channel located on the outer peripheral surface of the drive member.

[0012] According to one embodiment of the present invention, the driving member performs axial reciprocating motion under the drive of the driving device, and the driving member has teeth formed in the middle part, and the driving device drives the driving member through a gear set.

[0013] According to one embodiment of the present invention, the gear set includes a first gear shaft and a second gear shaft. A large gear and a first small gear are coaxially arranged on the first gear shaft, and a second small gear is arranged on the second gear shaft. The first small gear meshes with the driving member, the large gear meshes with the second small gear, and the second small gear is driven externally.

[0014] According to one embodiment of the present invention, the throttle valve assembly further includes a valve sleeve and a plug, the valve sleeve and the plug being disposed in the valve body, one end of the valve core near the drive member slidingly engaging with the valve sleeve, the other end of the valve core sliding along the plug, and a tapered surface formed on the outer surface of the valve core abutting against the valve sleeve.

[0015] According to one embodiment of the present invention, the outer diameters at both ends of the valve core and the diameter corresponding to the position where the valve core abuts are equal.

[0016] The present invention also provides a hydraulic system, comprising:

[0017] Hydraulic cylinder;

[0018] The dual throttle valve control module has one set of throttle valve assemblies controlling the lifting of the hydraulic cylinder, and another set of throttle valve assemblies controlling the lowering of the hydraulic cylinder.

[0019] According to one embodiment of the present invention, the valve body is provided with an oil inlet and an oil outlet for each group of throttle valve assemblies. One oil inlet introduces pressurized oil, and the corresponding oil outlet is unidirectionally connected to the rodless chamber of the hydraulic cylinder; the other oil inlet is connected to the rodless chamber of the hydraulic cylinder, and the corresponding oil outlet is connected to the oil tank.

[0020] Based on the above technical solution, the technical effects that the present invention can achieve are as follows:

[0021] 1. In the dual throttle valve control module of the present invention, the driving component is located between two sets of throttle valve assemblies, with a gap between it and the two valve cores. When the driving component moves to one side, it can push one valve core to open and control the opening degree, while the throttle valve assembly on the other side remains in its initial state; when the driving component moves to the other side, it can push the other valve core to open and control the opening degree, while one valve core remains in its initial state. That is, the driving component can control the opening degree of the throttle valve assemblies on both sides, and when the driving component controls the opening degree of one set of throttle valve assemblies, it will not cause the other set of throttle valve assemblies to move in tandem, thus realizing independent control of the two sets of throttle valve assemblies.

[0022] 2. The dual throttle valve control module of the present invention, by setting a through hole in the valve core to connect the two ends, can ensure that the pressure at both ends of the valve core is the same; a flow groove is formed on the drive component, and the cavity between the valve core and the drive component is connected to the oil return port through the flow groove, so that both ends of the valve core are in a low-pressure and connected state, and the movement of the valve core will not be affected by the uneven pressure on both sides, and the valve core response is fast and accurate; furthermore, the middle dimension of the drive component is reduced, which can reduce the precision machining area required for the sliding fit between the drive component and the inner wall of the valve body, making it easier to machine the drive component, and at the same time, it can keep the middle position of the drive component connected to the oil return port; the flow groove includes radial grooves and axial grooves, which can ensure the connection between the cavities and ensure the force balance of the drive component;

[0023] 3. The dual throttle valve control module of this invention uses a gear set to drive the driving component, achieving high precision and accurate control of the opening degree. Specifically, the gear set structure allows for precise control of the driving component's displacement through the transmission of large and small gears. Each displacement of the driving component corresponds to a change in the opening degree of the throttle valve assembly, thus enabling precise control of the throttle valve assembly's opening degree. The second small gear can be driven manually or electrically. In manual drive, the handle can be fixed to the second gear shaft, allowing adjustment of the corresponding throttle valve assembly's opening degree by manually operating the handle's angle. In electric drive, a high-response motor can be fixed to the second gear shaft. This not only allows for calculating the valve opening degree through the motor's rotation angle, thus enabling closed-loop control of the hydraulic cylinder piston's lifting and lowering speeds, but also allows for setting specific opening times for the two throttle valve assemblies within a short cycle (e.g., PWM pulse width modulation). Combined with position, speed, and force sensors, this enables precise control of the hydraulic cylinder piston's motion state.

[0024] 4. In the dual throttle valve control module of the present invention, the two ends of the valve core are slidably engaged with the valve sleeve and the screw plug, respectively. Setting the outer diameter of the end of the valve core that slidably engages with the screw plug to be equal to the diameter of the valve core abutting against the valve sleeve ensures that the pressure at the second oil port of the screw plug exerts the same force on the valve core in both axial directions, thus preventing the pressure at the second oil port of the screw plug from pressing the valve core tightly against the valve sleeve. Setting the outer diameter of the end of the valve core that slidably engages with the valve sleeve to be equal to the diameter of the valve core abutting against the valve sleeve ensures that the pressure at the first oil port of the valve sleeve exerts the same force on the valve core in both axial directions, thus preventing the pressure at the first oil port of the valve sleeve from pushing the valve core away from the valve sleeve. In other words, the above-mentioned diameter relationship ensures that the force exerted by the oil ports on the valve core of the throttle valve assembly is balanced, without affecting the movement of the valve core.

[0025] 5. The hydraulic system of this invention controls the oil inlet and return speeds of the hydraulic cylinder through a dual throttle valve control module, thereby controlling the lifting and lowering speeds of the hydraulic cylinder. Specifically, the connection between the oil port of the dual throttle valve control module and the hydraulic cylinder is configured such that when the driving component pushes the valve core of the throttle valve assembly controlling the lifting of the hydraulic cylinder to slide open, pressurized oil enters from the inlet to the outlet, then opens the check valve and enters the rodless chamber of the single-acting hydraulic cylinder, lifting the hydraulic cylinder piston at a certain speed. When the driving force is removed, the driving component returns to the neutral position, the throttle valve assembly closes, the pressurized oil is blocked, and the check valve is closed by the high-pressure oil in the rodless chamber of the hydraulic cylinder. The other throttle valve assembly is also closed, so the hydraulic cylinder piston can maintain its height for a longer period and will not continuously descend under gravity due to excessive oil leakage in the rodless chamber. Conversely, when the driving component pushes the valve core of the throttle valve assembly controlling the lowering of the hydraulic cylinder to slide open, the oil in the rodless chamber of the hydraulic cylinder enters from the corresponding inlet to the outlet and returns to the oil tank, causing the hydraulic cylinder piston to descend at a certain speed. Hydraulic lifting systems typically do not require both lifting and lowering valves to be fully open simultaneously, therefore this control module is highly compatible with hydraulic lifting systems. Attached Figure Description

[0026] Figure 1 is a schematic diagram of the dual throttle valve control module;

[0027] Figure 2 is a cross-sectional view of the dual throttle valve control module;

[0028] Figure 3 is a magnified view of a portion of Figure 2;

[0029] Figure 4 is a schematic diagram of the structure of the drive component and the gear set;

[0030] Figure 5 is a schematic diagram of the drive component;

[0031] Figure 6 is a hydraulic schematic diagram of the hydraulic system;

[0032] In the diagram: 1-Valve body; 11-Inlet; 12-Outlet; 13-Return port; 14-Mounting cavity; 2-Throttle valve assembly; 21-Valve core; 211-Through hole; 212-First end; 213-Second end; 214-Conical surface; 215-Annular protrusion; 22-Elastic element; 23-Valve sleeve; 231-First oil port; 24-Plug; 241-Second oil port; 25-First cavity; 26-Second cavity; 271-First seal; 272- Second seal; 273-Third seal; 28-Gasket; 3-Driver; 31-Flow groove; 311-Radial groove; 312-Axial groove; 32-Gear; 33-Cut surface; 34-Circumferential surface; 4-Gear set; 41-First gear shaft; 42-Large gear; 43-First pinion; 44-Second gear shaft; 45-Second pinion; 5-Hydraulic cylinder; 51-Piston; 52-Rod chamber; 53-Rodless chamber; 6-Check valve; 7-Oil tank. Detailed Implementation

[0033] 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.

[0034] 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.

[0035] 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.

[0036] 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.

[0037] 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.

[0038] 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.

[0039] As shown in Figures 1-5, this embodiment proposes a dual throttle valve control module, including a valve body 1, a throttle valve assembly 2, and a drive unit 3. The valve body 1 is provided with multiple oil ports. The throttle valve assembly 2 consists of two sets, which are symmetrically arranged inside the valve body 1. In the initial state, the valve core 21 of the throttle valve assembly 2 forms abutment under the action of the elastic member 22 to block the communication between the oil ports. The drive unit 3 is located between the two sets of throttle valve assemblies 2. There is a gap between the two ends of the drive unit 3 and the two valve cores 21. The axial movement of the drive unit 3 can push one side of the valve core 21 to open to control the opening degree, while the other side of the valve core 21 remains in the initial state.

[0040] As shown in Figures 1-2, a mounting cavity 14 is formed inside the valve body 1 to facilitate the assembly of the throttle valve assembly 2 and the drive component 3. Multiple oil ports are formed on the valve body 1, each communicating with the mounting cavity 14. Specifically, for each throttle valve assembly 2, the valve body 1 is provided with an oil inlet 11 and an oil outlet 12. The valve core 21 of the throttle valve assembly 2 abuts against the elastic element 22, blocking the communication between the corresponding oil inlet 11 and oil outlet 12.

[0041] As a preferred technical solution in this embodiment, the mounting cavity 14 penetrates the valve body 1, and the central space of the mounting cavity 14 is enlarged to facilitate the assembly of the gear set 4.

[0042] As a preferred embodiment, the oil inlet 11 and oil outlet 12 of the two sets of throttle valve assemblies 2 are located at both ends of the valve body 1 and are symmetrically arranged. The valve body 1 can be configured as a symmetrical structure.

[0043] As a preferred technical solution in this embodiment, the valve body 1 is provided with an oil return port 13, which is located in the middle of the valve body 1.

[0044] As a preferred technical solution in this embodiment, the positions of the oil inlet 11 and oil outlet 12 corresponding to each group of throttle valve assembly 2 can be interchanged. The oil inlet 11 can be set to be located on the axial outer side of the oil outlet 12, or the oil inlet 11 can be set to be located on the axial inner side of the oil outlet 12.

[0045] Two sets of throttle valve assemblies 2 are symmetrically distributed within the valve body 1. The two sets of throttle valve assemblies 2 control the on / off state and opening degree between the two sets of oil inlet ports 11 and oil outlet ports 12, respectively. Taking one set of throttle valve assembly 2 as an example, as shown in Figure 3, the throttle valve assembly 2 includes a valve core 21, an elastic element 22, a valve sleeve 23, and a screw plug 24. The valve sleeve 23 is located inside the screw plug 24, and the screw plug 24 is used to seal the opening at the end of the mounting cavity 14. One end of the valve core 21 slides in cooperation with the valve sleeve 23, and the other end of the valve core 21 slides along the screw plug 24. A conical surface 214 is formed on the outer surface of the valve core 21. Under the action of the elastic element 22, the conical surface 214 abuts against the valve sleeve 23, disconnecting the connection between the oil inlet port 11 and the oil outlet port 12.

[0046] As a preferred technical solution of this embodiment, the valve sleeve 23 is located on the inner circumference of one of the oil ports, the oil inlet 11 and the oil outlet 12. The valve sleeve 23 is provided with a first oil port 231 to facilitate communication with one of the corresponding oil ports, the oil inlet 11 and the oil outlet 12. The screw plug 24 extends to the inner circumference of the other oil port, the oil inlet 11 and the oil outlet 12. The screw plug 24 is provided with a second oil port 241 to facilitate communication with the other oil port, the oil outlet 12 and the oil inlet 11. When the oil inlet 11 is located axially outside the oil outlet 12, the valve sleeve 23 is located on the inner circumference of the oil outlet 12, the first oil port 231 on the valve sleeve 23 communicates with the oil outlet 12, the screw plug 24 extends to the inner circumference of the oil inlet 11, and the second oil port 241 on the screw plug 24 communicates with the oil inlet 11; when the oil inlet 11 is located axially inside the oil outlet 12, the valve sleeve 23 is located on the inner circumference of the oil inlet 11, the first oil port 231 on the valve sleeve 23 communicates with the oil inlet 11, the screw plug 24 extends to the inner circumference of the oil outlet 12, and the second oil port 241 on the screw plug 24 communicates with the oil outlet 12. In this embodiment, the oil inlet 11 is located axially outside the oil outlet 12, the valve sleeve 23 is located on the inner circumference of the oil outlet 12, the first oil port 231 communicates with the oil outlet 12, the screw plug 24 extends to the inner circumference of the oil inlet 11, and the second oil port 241 communicates with the oil inlet 11.

[0047] As a preferred embodiment, a first annular cavity is formed between the valve core 21 and the valve sleeve 23 in the circumferential direction, and the first annular cavity communicates with the first oil port 231; a second annular cavity is formed between the screw plug 24 and the valve core 21 in the circumferential direction, and the second annular cavity communicates with the second oil port 241. The conical surface 214 of the valve core 21 abuts against the end of the valve sleeve 23 near the screw plug 24, blocking the communication between the first annular cavity and the second annular cavity, thereby blocking the communication between the oil inlet 11 and the oil outlet 12.

[0048] As a preferred technical solution of this embodiment, the valve core 21 is rod-shaped with varying outer diameter. The valve core 21 has a cylindrical first end 212 and a second end 213. The first end 212 of the valve core 21 is slidably engaged with the end of the valve sleeve 23 away from the screw plug 24, and the second end 213 of the valve core 21 is slidably engaged with the end of the screw plug 24 away from the valve sleeve 23. A tapered surface 214 is formed on the outer surface of the middle part of the valve core 21. Preferably, to prevent the pressure at the oil outlet 12 from pushing the valve core 21 away from the valve sleeve 23, the diameter D1 of the first end 212 of the valve core 21 is set to be equal to the diameter D3 of the abutment point of the conical surface 214. In this way, the oil entering the first annular cavity has the same area of ​​action and the same force in both axial directions, thereby preventing the pressure at the oil outlet 12 from pushing the valve core 21 away from the valve sleeve 23. To prevent the pressure at the oil inlet 11 from pressing the valve core 21 onto the valve sleeve 23, the diameter D2 of the second end 213 of the valve core 21 is set to be equal to the diameter D3 of the abutment point of the conical surface 214. In this way, the oil entering the second annular cavity has the same area of ​​action and the same force in both axial directions, thereby preventing the pressure at the oil inlet 11 from pressing the valve core 21 onto the valve sleeve 23.

[0049] As a preferred embodiment, a first cavity 25 is formed between the first end 212 of the valve core 21 and the driving member 3, and a second cavity 26 is formed between the second end 213 of the valve core 21 and the screw plug 24. In order to ensure pressure balance between the two cavities, a through hole 211 is provided on the valve core 21 to connect the first cavity 25 and the second cavity 26. Preferably, the through hole 211 is an axially extending through hole.

[0050] In a preferred embodiment, one end of the elastic element 22 abuts against the screw plug 24, and the other end acts on the valve core 21. Preferably, the elastic element 22 can be sleeved on the valve core 21, a first sealing element 271 is provided between the screw plug 24 and the valve core 21, and is limited by a gasket 28. An annular protrusion 215 is formed on the outer peripheral surface of the valve core 21. One end of the elastic element 22 abuts against the gasket 28, and the other end of the elastic element 22 abuts against the annular protrusion 215. In the initial state, the elastic element 22 is in a pre-compressed state. The elastic element 22 can be, but is not limited to, a spring.

[0051] As a preferred technical solution in this embodiment, in order to ensure the overall sealing performance, a second sealing element 272 is provided between the valve sleeve 23 and the inner wall of the valve body 1, and the second sealing element 272 is located between the oil inlet 11 and the oil outlet 12; a third sealing element 273 is provided between the screw plug 24 and the inner wall of the valve body 1.

[0052] As shown in Figure 1-2, the drive component 3 is used to push the valve core 21 of the throttle valve assemblies 2 on both sides to control the opening. The drive component 3 is located between the two sets of throttle valve assemblies 2 and is coaxially arranged with the two sets of throttle valve assemblies 2. The two ends of the drive component 3 are slidably engaged with the valve body 1, and the middle part of the drive component 3 is driven to perform axial reciprocating motion.

[0053] As a preferred technical solution of this embodiment, as shown in FIG5, the driving member 3 is a rod-shaped structure, and the two ends of the driving member 3 have circumferential surfaces 34, which facilitate sliding cooperation with the inner wall of the mounting cavity 14.

[0054] As a preferred technical solution of this embodiment, as shown in FIG5, the middle dimension of the driving member 3 is reduced, and the outer diameter of the middle part of the driving member 3 is reduced compared with the two ends. In this way, a cavity is formed on the outer periphery of the middle part of the driving member 3, which facilitates communication with the oil return port 13.

[0055] As a preferred technical solution in this embodiment, as shown in FIG5, the driving member 3 also has teeth 32 formed in the middle, which facilitates being driven by tooth transmission.

[0056] As a preferred technical solution in this embodiment, as shown in FIG5, a cross-section 33 is formed in the middle of the driving member 3. Correspondingly, a planar protrusion can be provided on the inner wall of the valve body 1. The planar protrusion is in clearance fit with the cross-section 33. Once the driving member 3 deflects at an angle, the planar protrusion can abut against the cross-section 33 to prevent it from rotating. In addition, a stepped surface is formed between the cross-section 33 and the outer peripheral surface of the middle part of the driving member 3. The planar protrusion can also cooperate with the stepped surface to limit the movement range of the driving member 3.

[0057] As a preferred technical solution in this embodiment, as shown in FIG5, the two ends of the driving member 3 are formed with flow grooves 31, which facilitates the communication between the first cavity 25 and the oil return port 13 through the flow grooves 31. The flow grooves 31 extend from the end face of the driving member 3 to the middle. Specifically, the flow grooves 31 include radial grooves 311 and axial grooves 312. The radial grooves 311 penetrate the end face of the driving member 3 in the radial direction. The axial grooves 312 can be set as two, which are respectively connected to the two ends of the radial grooves 311 and extend parallel to the axial direction. The radial grooves 311 on the end face can ensure that when the driving member 3 abuts against the valve core 21, the oil in the first cavity 25 can still be connected to the oil return port 13 through the flow grooves 31.

[0058] As a preferred technical solution in this embodiment, as shown in FIG5, the driving component 3 has a symmetrical structure.

[0059] As shown in Figure 4, the driving component 3 reciprocates axially under the drive of the driving device. The driving device can drive the driving component 3 through the gear set 4. Specifically, the gear set 4 includes a first gear shaft 41 and a second gear shaft 44. A large gear 42 and a first small gear 43 are coaxially arranged on the first gear shaft 41, and a second small gear 45 is arranged on the second gear shaft 44. The first small gear 43 meshes with the teeth 32 on the driving component 3, and the second small gear 45 meshes with the large gear 42. By externally driving the second gear shaft 44 and the second small gear 45, the driving component 3 can be driven to reciprocate axially. By adopting a small gear-large gear-small gear transmission method, precise control of the movement of the driving component 3 can be achieved.

[0060] As a preferred technical solution in this embodiment, the second gear shaft 44 can be manually driven. The driving device can be a handle, which is connected to the second gear shaft 44. The second gear shaft 44 can be driven to rotate by controlling the angle of the handle, thereby transmitting power to the driving member 3. Alternatively, the second gear shaft 44 can also be electrically driven. The driving device can be a high-response motor, which can be connected to the second gear shaft 44. The axial movement position of the driving member 3 can be closed-loop controlled by the rotation angle of the motor. Furthermore, the position of the driving member 3 can be precisely controlled by PWM pulse width modulation combined with sensor detection.

[0061] As a preferred technical solution in this embodiment, in addition to using gear transmission, the axial movement of the driving component 3 can also be controlled by using a lead screw and nut drive method, a cam-connecting rod engagement method, etc.

[0062] As shown in Figure 6, this embodiment also provides a hydraulic system, including the aforementioned dual throttle valve control module, and a hydraulic cylinder 5. The hydraulic cylinder 5 is connected to the dual throttle valve control module, and the dual throttle valve control module controls the lifting and lowering speed of the hydraulic cylinder 5.

[0063] The hydraulic cylinder 5 includes a piston 51 located inside the cylinder body. The piston 51 divides the inside of the cylinder body into a rod chamber 52 and a rodless chamber 53. When oil enters the rodless chamber 53, it can push the piston 51 to rise; when oil returns from the rodless chamber 53, the piston 51 descends.

[0064] Hydraulic cylinder 5 is connected to the oil port on the dual throttle valve control module. One set of throttle valve components 2 of the dual throttle valve control module controls the hydraulic cylinder 5 to rise, and the other set of throttle valve components 2 controls the hydraulic cylinder 5 to fall.

[0065] Specifically, for clarity, the two sets of throttle valve assemblies 2 in the dual throttle valve control module are the first set of throttle valve assemblies 2 and the second set of throttle valve assemblies 2, respectively. The first set of throttle valve assemblies 2 can be configured to introduce pressurized oil through its corresponding inlet port 11 and connect its corresponding outlet port 12 to the rodless chamber 53 of the hydraulic cylinder 5. The first set of throttle valve assemblies 2 controls the oil inlet speed of the rodless chamber 53 of the hydraulic cylinder 5, thereby controlling the upward movement speed of the piston 51. The second set of throttle valve assemblies 2 connects its corresponding inlet port 11 to the rodless chamber 53 of the hydraulic cylinder 5 and connects its corresponding outlet port 12 to the oil tank 7. The second set of throttle valve assemblies 2 controls the oil return speed of the rodless chamber 53 of the hydraulic cylinder 5, thereby controlling the downward movement speed of the piston 51.

[0066] As a preferred technical solution in this embodiment, a one-way valve 6 is provided between the oil outlet 12 of the first group of throttle valve assembly 2 and the rodless chamber 53 to control the pressure oil to flow unidirectionally to the rodless chamber 53, and not to flow in reverse.

[0067] As a preferred technical solution in this embodiment, the rod chamber 52 is connected to the oil tank 7. When the piston 51 moves upward, the rod chamber 52 discharges oil into the oil tank 7; when the piston 51 moves downward, the oil tank 7 can replenish the rod chamber 52 with oil.

[0068] As a preferred technical solution in this embodiment, the oil return port 13 is connected to the oil tank 7, so that the first chamber 25, the second chamber 26, and the flow groove 31 of the drive component 3 are all in a low-pressure state.

[0069] Based on the above technical solution, the working principle of the hydraulic system in this embodiment is as follows:

[0070] As shown in Figure 6, when the drive unit 3 moves to a certain position to the right, the valve port of the first set of throttle valve assembly 2 is opened, and the pressure oil in the oil inlet 11 enters. Then, the check valve 6 is opened to enter the rodless chamber 53 of the hydraulic cylinder 5, which lifts the piston 51 of the hydraulic cylinder 5 at a certain speed. When the driving force is removed, the drive unit 3 returns to the neutral position, the valve port of the first set of throttle valve assembly 2 is closed, the pressure oil in the oil inlet 11 is blocked, and the check valve 6 is closed by the high pressure oil in the rodless chamber 53 of the hydraulic cylinder 5. The second set of throttle valve assembly 2 remains in the open state. Therefore, the piston 51 of the hydraulic cylinder 5 can maintain its height for a longer period of time and will not continue to fall under the action of gravity due to excessive oil leakage in the rodless chamber 53.

[0071] When the drive unit 3 moves to a certain position to the left, the valve port of the second set of throttle valve assembly 2 is opened, and the oil in the rodless chamber 53 of the hydraulic cylinder 5 enters from the oil inlet 11 and then returns to the oil tank 7 through the oil outlet 12. The piston 51 of the hydraulic cylinder 5 descends at a certain speed. Usually, the hydraulic lifting system does not require both the lifting and lowering valve ports to be fully open at the same time, so the compatibility of this control module with the hydraulic lifting system is very high.

[0072] Each displacement of the drive component 3 corresponds to a specific opening of one of the two sets of throttle valve assemblies 2, thus the lifting and lowering speeds of the piston 51 in the hydraulic cylinder 5 are continuously controllable. Generally, the transmission mechanism of this control module can be manually driven or driven by a motor. By fixing the handle to the second gear shaft 44, the lifting and lowering speeds of the piston 51 in the hydraulic cylinder 5 can be proportionally controlled by the angle of the handle. If a high-response motor is fixed to the second gear shaft 44, not only can the valve opening be calculated by the angle of motor rotation, thereby enabling closed-loop control of the lifting and lowering speeds of the piston 51 in the hydraulic cylinder 5, but also a specific opening time (such as PWM pulse width modulation) can be set for the two throttle valve assemblies 2 within a short cycle. Combined with position, speed, and force sensors, the motion state of the piston 51 can be precisely controlled.

[0073] 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 dual throttle valve control module, characterized in that, include: Valve body (1), wherein multiple oil ports are provided on the valve body (1); Throttling valve assembly (2), the throttle valve assembly (2) consists of two sets, symmetrically arranged in the valve body (1), the throttle valve assembly (2) includes a valve core (21), the valve core (21) forms abutment under the action of elastic element (22) to block the communication between oil ports; A drive (3) is located between two sets of throttle valve assemblies (2). The two ends of the drive (3) are respectively separated from the two valve cores (21). The drive (3) pushes the valve core (21) on one side to open in order to control the opening degree. The valve core (21) has a through hole (211) connecting both ends, and the drive member (3) has a flow groove (31). The cavity between the valve core (21) and the drive member (3) is connected to the return oil port (13) through the flow groove (31).

2. The dual throttle valve control module according to claim 1, characterized in that, The middle part of the drive member (3) is reduced in size and connected to the oil return port (13). The two ends of the drive member (3) form the flow groove (31), which extends from the end face of the drive member (3) to the middle part of the drive member (3).

3. The dual throttle valve control module according to claim 2, characterized in that, The flow channel (31) includes a radial channel (311) located on the end face of the drive member (3) and an axial channel (312) located on the outer peripheral surface of the drive member (3).

4. A dual throttle valve control module according to any one of claims 1-3, characterized in that, The driving member (3) performs axial reciprocating motion under the drive of the driving device. The driving member (3) has teeth (32) formed in the middle. The driving device drives the driving member (3) through a gear set (4).

5. A dual throttle valve control module according to claim 4, characterized in that, The gear set (4) includes a first gear shaft (41) and a second gear shaft (44). A large gear (42) and a first small gear (43) are coaxially arranged on the first gear shaft (41), and a second small gear (45) is arranged on the second gear shaft (44). The first small gear (43) meshes with the driving member (3), and the large gear (42) meshes with the second small gear (45). The second small gear (45) is driven externally.

6. The dual throttle valve control module according to claim 1, characterized in that, The throttle valve assembly (2) further includes a valve sleeve (23) and a screw plug (24). The valve sleeve (23) and the screw plug (24) are disposed inside the valve body (1). One end of the valve core (21) near the drive member (3) is slidably engaged with the valve sleeve (23), and the other end of the valve core (21) slides along the screw plug (24). A tapered surface (214) is formed on the outer surface of the valve core (21) and abuts against the valve sleeve (23).

7. A dual throttle valve control module according to claim 1 or 6, characterized in that, The outer diameters at both ends of the valve core (21) and the diameter corresponding to the position where the valve core (21) abuts are all equal.

8. A hydraulic system, characterized in that, include: Hydraulic cylinder (5); According to any one of claims 1-7, in the dual throttle valve control module, one set of the throttle valve assemblies (2) controls the hydraulic cylinder (5) to rise, and the other set of throttle valve assemblies (2) controls the hydraulic cylinder (5) to fall.

9. A hydraulic system according to claim 8, characterized in that, The valve body (1) is provided with an oil inlet (11) and an oil outlet (12) for each throttle valve assembly (2). One oil inlet (11) introduces pressurized oil, and the corresponding oil outlet (12) is unidirectionally connected to the rodless chamber (53) of the hydraulic cylinder (5); the other oil inlet (11) is connected to the rodless chamber (53) of the hydraulic cylinder (5), and the corresponding oil outlet (12) is connected to the oil tank (7).

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