Novel flow adjusting device
By employing a variable-area dual-nozzle pressure-splitting structure and a solenoid valve combination in the flow regulating device, the problems of poor flow regulation accuracy and large step span are solved, achieving high-precision and diversified flow control, and possessing solenoid valve fault redundancy capability.
Patent Information
- Application Number
- CN202520849932.7
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-04-30
- Publication Date
- 2026-02-17
- Estimated Expiration
- 2035-04-30
AI Technical Summary
Existing flow regulation devices have poor flow regulation accuracy, large flow step range, and conventional drive methods have low reliability or insufficient driving force.
A novel flow regulation device is adopted, which forms a variable area dual-nozzle pressure-dividing structure by setting a valve core and an electromagnetic component inside the housing. Combined with the elastic force provided by the spring, the valve core is controlled to move within the housing, thereby achieving multi-stage precise pressure regulation. By using different opening degrees of the electromagnetic valve to form multi-stage fluid pressure, the precise movement of the valve core is ensured, and multi-stage small-span flow regulation is achieved.
It achieves high-precision flow regulation with a small flow step range, diverse control methods, wide applicability, redundancy, and high reliability, and can still achieve precise control even when the solenoid valve fails.
Smart Images
Figure CN223923882U_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The utility model belongs to valve flow control technical field, concretely relates to a novel flow regulating device. BACKGROUND
[0002] For the regulation of fuel flow, the conventional regulator adopts three driving modes of high-speed valve, servo valve or motor, the regulation precision of high-speed valve is poor, the reliability of servo valve is low and sensitive to pollution, among them, both high-speed valve and servo valve need to be controlled in closed loop, although the motor can realize open loop control, the driving force is small, the flow regulation precision of the above three flow control modes is poor and the flow step span is large. SUMMARY
[0003] The utility model discloses a novel flow regulating device to solve the poor flow regulation precision and large flow step span of the existing flow regulating device.
[0004] The utility model discloses the following technical scheme: a novel flow regulating device, including a hollow column's casing, be provided with a valve core in the casing, the casing is isolated as two chambers through the valve core in the casing, and is control chamber and thrust chamber respectively, control chamber is provided with control inlet electromagnetic group and control outlet electromagnetic group respectively, spring is provided with in thrust chamber, and the both ends of spring are connected to the valve core and the inner wall of casing respectively, the coaxial annular groove is seted up on the valve core, and the annular groove forms the flow liquid groove with the inner wall of casing, the outer wall of casing is provided with the liquid inlet channel and liquid outlet channel apart,
[0005] Among them, control inlet electromagnetic group and control outlet electromagnetic group are used for controlling the pressure in control chamber by controlling the fluid flow in control chamber, the valve core is used for realizing the reciprocating movement of the valve core in the casing along its axial direction under the action of the pressure change in control chamber, and forms two limit positions of first limit position and second limit position, the flow liquid groove is used for being communicated with the liquid inlet channel and not being communicated with the liquid outlet channel to close the valve when being in the first limit position, and the flow liquid groove is also used for being communicated with the liquid inlet channel and the liquid outlet channel to open the valve when being in the second limit position.
[0006] Further, the number of electromagnetic valves in control inlet electromagnetic group is greater than the number of electromagnetic valves in control outlet electromagnetic group.
[0007] Further, the proportion of the electromagnetic valve opening degree of control inlet electromagnetic group and the electromagnetic valve opening degree of control outlet electromagnetic group is 1-9.
[0008] Further, the spring is coaxially arranged with the valve core.
[0009] Further, the width of the flow liquid groove is L1, the distance between the outermost side of the liquid inlet channel and the outermost side of the liquid outlet channel is L2, and L1≥L2.
[0010] Further, the inner diameters of the liquid inlet channel and the liquid outlet channel are equal.
[0011] The beneficial effects of the utility model are as follows: the inside of the shell is divided into a control cavity and a thrust cavity by installing a valve core, an elastic force is provided by a spring located in the thrust cavity at one end of the valve core, a variable area double-nozzle pressure division structure is formed by a plurality of electromagnetic valves in the control-in electromagnetic group and the control-out electromagnetic group, and the fluid entering rate and the fluid leading-out rate are controlled, so that different pressures are formed in the control cavity, the mutual cooperation of different opening degrees of the plurality of electromagnetic valves in the control-in electromagnetic group and the control-out electromagnetic group is used to form multi-step precise pressure, the valve core is pushed by the multi-step fluid pressure, the movement value of the valve core in the shell is controlled, the flow grooves on the valve core correspond to the liquid inlet channel and the liquid outlet channel, the flow channels with different cross-sectional areas are formed, and then multi-step small-span precise flow regulation is realized, the flow regulation control precision is high, the flow step span is small, and the control mode is various. BRIEF DESCRIPTION OF DRAWINGS
[0012] Figure 1 It is a structural schematic view of the novel flow regulating device of the utility model;
[0013] Figure 2 It is a structural schematic view of the valve core located at the first limiting position of the utility model;
[0014] Figure 3 It is a structural schematic view of the valve core located at the second limiting position of the utility model.
[0015] 1, shell; 2, control cavity; 3, valve core; 4, flow groove; 5, spring; 6, liquid inlet channel; 7, liquid outlet channel; 8, control-in electromagnetic group; 9, control-out electromagnetic group, 10. thrust cavity, 11. boss, 12. stopper.
DETAILED DESCRIPTION
[0016] The utility model will be explained in detail in combination with the drawings and specific embodiments.
[0017] The utility model provides a novel flow regulating device, as shown in the figure, comprising a hollow cylindrical shell 1, a valve core 3 is arranged in the shell 1, the shell 1 is isolated into two cavities, i.e. control cavity 2 and thrust cavity 10 by the valve core 3. Figure 1
[0018] The control chamber 2 is connected to the inlet electromagnetic assembly 8 and the outlet electromagnetic assembly 9, respectively. A spring 5 is installed in the thrust chamber 10, with its two ends connected to the valve core 3 and the inner wall of the housing 1, respectively. An annular groove is coaxially formed on the valve core 3, and a flow channel 4 is formed between the annular groove and the inner wall of the housing 1. An inlet channel 6 and an outlet channel 7 are spaced apart on the outer wall of the housing 1.
[0019] The inlet solenoid assembly 8 and the outlet solenoid assembly 9 are used to regulate the pressure inside the control chamber 2 by controlling the flow rate of fluid entering and exiting the control chamber 2. The inlet solenoid assembly 8 and the outlet solenoid assembly 9 are used to control the fluid entry rate and exit rate, respectively, so that different pressures are formed inside the control chamber 2 to drive the valve core 3 to move.
[0020] The valve core 3 is used to reciprocate along its axis inside the housing 1 under the action of pressure changes within the control chamber 2, forming two extreme positions: a first extreme position and a second extreme position. The position of the valve core 3 closest to the control chamber 2 is the first extreme position, and the position closest to the thrust chamber 10 is the second extreme position. The liquid inlet channel 6 is located on the side closest to the control chamber 2, and the liquid outlet channel 7 is located on the side closest to the thrust chamber 10.
[0021] The flow channel 4 is used to connect with the inlet channel 6 but not with the outlet channel 7 to close the valve at the first limit position; the flow channel 4 is also used to connect with both the inlet channel 6 and the outlet channel 7 to open the valve at the second limit position. The annular flow channel 4 ensures uniform distribution of fluid within it, avoiding turbulence and eddies during fluid flow, further improving the accuracy and stability of flow control. The structure of the annular channel allows fluid to flow smoothly into the inlet channel 6, and after precise control by the valve core 3, it flows steadily out of the outlet channel 7, making the entire flow process more efficient and orderly.
[0022] A boss 11 is provided inside the housing 1 near the control chamber 2 to limit the first extreme position of the valve core 3. A stop 12 is provided inside the thrust chamber 10 to limit the second extreme position of the valve core 3.
[0023] In some embodiments, the number of solenoid valves in the inlet solenoid group 8 is greater than the number of solenoid valves in the outlet solenoid group 9. Since the fluid flow rate within the solenoid valves is the same, controlling the opening degrees of the solenoid valves in the inlet and outlet solenoid groups 8 and 9 controls the fluid inflow and outflow rates, creating different pressures within the control chamber 2 to move the valve core 3. This difference in the number of solenoid valves between the inlet and outlet solenoid groups 8 not only improves the flexibility of flow control but also enhances the redundancy of the device. Furthermore, the consistency of the fluid flow rate within the solenoid valves ensures the accuracy and predictability of flow control, allowing the entire device to perform well even under complex and variable operating conditions. In practical applications, the number of solenoid valves in the inlet solenoid group 8 can be set to three, and the number of solenoid valves in the outlet solenoid group 9 can be set to five, resulting in 2 out of 8 solenoid valves. 8 =256 different states, theoretically there are 256 ratios, so the whole device can have 256 state points, which is equivalent to the theoretical minimum movement distance of the valve position being 0.4%.
[0024] In some embodiments, the ratio of the opening degree of the solenoid valve in the inlet solenoid group 8 to the opening degree of the solenoid valve in the outlet solenoid group 9 is 1 to 9. In actual use, for example, the opening ratio can be set to 1, 2, 5 or 9. By using different opening ratios of the solenoid valve in the inlet solenoid group 8 and the solenoid valve in the outlet solenoid group 9, more precise fluid pressure can be achieved, thereby controlling the valve core 3 to move precisely, controlling the flow rate more accurately, and achieving better performance.
[0025] In some embodiments, the spring 5 is coaxially arranged with the valve core 3. Arranging the valve core 3 and spring 5 on the same axis makes the valve core 3 more stable during movement, reducing the possibility of wobbling and deviation. The spring 5 helps the valve core 3 quickly and accurately return to its initial position, preparing it for the next opening.
[0026] In some embodiments, the width of the flow channel 4 is L1, and the distance between the outermost edge of the inlet channel 6 and the outermost edge of the outlet channel 7 is L2, where L1 ≥ L2. The width of the flow channel 4 matches the width distribution of the inlet channel 6 and the outlet channel 7 according to the above conditions, ensuring that when the valve core 3 moves to a certain position, it can connect the flow channel 4 with the inlet channel 6 and the outlet channel 7, thereby opening the valve.
[0027] In some embodiments, the inner diameters of the inlet channel 6 and the outlet channel 7 are equal. Equal inner diameters of the inlet channel 6 and the outlet channel 7 ensure that the flow rate of the fluid remains consistent when entering and exiting the valve, avoiding flow loss or pressure changes caused by differences in diameter. This further improves the overall performance of the valve and the accuracy of flow control. At the same time, the equal inner diameter design simplifies the valve manufacturing process and reduces production costs.
[0028] The working method of the novel flow regulating device of this utility model is as follows:
[0029] Fluid is introduced into control chamber 2 through multiple solenoid valves in the inlet solenoid assembly 8. The inlet and outlet solenoid assemblies 8 and 9 form a variable-area dual-nozzle pressure-dividing structure, controlling the fluid inflow and outflow rates within control chamber 2 to create different pressures. Since the inlet pressure before inlet solenoid assembly 8 and the outlet pressure after outlet solenoid assembly 9 are already determined, the pressure within control chamber 2 is only related to the throttling areas of the inlet and outlet.
[0030]
[0031] According to the formula above, by controlling different solenoid valve switches, different ratios of inlet and outlet area can be formed, thereby enabling the pressure in control chamber 2 to reach the target value.
[0032] Driven by different pressures, the valve core 3 will move within the housing 1, such as... Figure 2 As shown, when valve core 3 moves to the first limit position, the liquid flow channel 4 is connected to the inlet channel 6, but not to the outlet channel 7, and the valve is closed at this time. Figure 3 As shown, when the valve core 3 moves to the second limit position, the flow channel 4 is also used to connect with both the inlet channel 6 and the outlet channel 7 at the second limit position to open the valve. At the same time, as the valve core 3 moves from the first limit position to the second limit position, the flow channel 4 remains connected to the inlet channel 6, and the connection area between the flow channel 4 and the outlet channel 7 gradually increases until the valve core 3 moves to the second limit position.
[0033] This invention utilizes a series of solenoid valves, consisting of an inlet solenoid assembly 8 and an outlet solenoid assembly 9, to form a variable-area dual-nozzle pressure-dividing structure. It controls the fluid inflow and outflow rates within the control chamber 2, creating different pressures within the chamber. The different opening degrees of the solenoid valves in the inlet and outlet solenoid assemblies 8 and 9 work together to create multi-stage precise pressure. These multi-stage fluid pressures drive the valve core 3, controlling its movement within the control chamber 2. This allows the flow groove 4 on the valve core 3 to correspond with the inlet channel 6 and the outlet channel 7, forming different flow channels. This achieves multi-stage, small-span precise flow regulation, resulting in high flow regulation control accuracy, small flow step spans, and diverse control methods.
[0034] When one of the solenoid valves in the inlet solenoid group 8 and the outlet solenoid group 9 fails to work properly due to a malfunction, the system can quickly adjust the opening of other solenoid valves. The remaining solenoid valves can also achieve multi-stage precise flow control. It has a wide range of applications and good performance.
Claims
1. A novel flow regulating device, characterized in that, The device includes a hollow cylindrical shell (1), inside which a valve core (3) is disposed. The shell (1) is divided into two chambers by the valve core (3), namely a control chamber (2) and a thrust chamber (10). The control chamber (2) is connected to an inlet electromagnetic group (8) and an outlet electromagnetic group (9). The thrust chamber (10) is provided with a spring (5), the two ends of which are connected to the valve core (3) and the inner wall of the shell (1). The valve core (3) is coaxially provided with an annular groove, which forms a flow channel (4) between the annular groove and the inner wall of the shell (1). The outer wall of the shell (1) is provided with an inlet channel (6) and an outlet channel (7) spaced apart. The inlet electromagnetic assembly (8) and outlet electromagnetic assembly (9) are used to regulate the pressure in the control chamber (2) by controlling the flow rate of fluid entering and exiting the control chamber (2); the valve core (3) is used to reciprocate along its axis inside the housing (1) under the action of pressure change in the control chamber (2), and form two extreme positions: a first extreme position and a second extreme position; the flow channel (4) is used to connect with the inlet channel (6) in the first extreme position, but not to connect with the outlet channel (7) to close the valve; the flow channel (4) is also used to connect with both the inlet channel (6) and the outlet channel (7) in the second extreme position to open the valve.
2. The novel flow regulating device as described in claim 1, characterized in that, The number of solenoid valves in the inlet solenoid group (8) is greater than the number of solenoid valves in the outlet solenoid group (9).
3. The novel flow regulating device as described in claim 2, characterized in that, The ratio of the opening degree of the solenoid valve of the inlet control solenoid group (8) to the opening degree of the solenoid valve of the outlet control solenoid group (9) is 1 to 9.
4. A novel flow regulating device as described in any one of claims 1-3, characterized in that, The spring (5) is coaxially arranged with the valve core (3).
5. A novel flow regulating device as described in claim 4, characterized in that, The width of the liquid flow channel (4) is L1, and the distance between the outermost edge of the liquid inlet channel (6) and the outermost edge of the liquid outlet channel (7) is L2, where L1 ≥ L2.
6. The novel flow regulating device as described in claim 5, characterized in that, The inner diameters of the inlet channel (6) and the outlet channel (7) are equal.