High-precision adjustable anti-backflow spring nozzle

Abstract

The utility model discloses a high-precision adjustable anti-backflow spring nozzle: including annular nozzle, the inside coaxial line of annular nozzle is equipped with spout valve element, the annular spiral flow pressure chamber between spout valve element and annular nozzle, the inner edge of annular nozzle injection end and the outer edge between spout valve element form annular injection gap, the water pressure in spiral flow pressure chamber can drive spout valve element do along the axial direction movement, make the width of annular injection gap increase, the wall body of annular nozzle is away from the one side of injection end and is equipped with a plurality of spiral flow channel in the circumference array, the liquid outlet of each spiral flow channel is connected spiral flow pressure chamber, and the water flow of a plurality of spiral flow channels that surge into spiral flow pressure chamber can drive the liquid in spiral flow pressure chamber to form spiral flow, can adjust the pressure in the infusion device according to the running state of production equipment, thereby adjusting the injection opening of nozzle, thereby adjusting the cooling liquid flow that sprays, can effectively prevent the equipment damage caused by not in time cooling, cooling liquid backflow and so on accident.

Description

Technical Field

[0001] This utility model belongs to the field of boiler thermal system equipment, and more specifically, it is a high-precision adjustable anti-backflow spring nozzle. Background Technology

[0002] In some industrial production workshops that use boilers, the ambient temperature will change with the operating status of the production equipment and the outside temperature. However, the flow rate of traditional cooler nozzles is usually fixed. Therefore, when the temperature inside the equipment is too high, the fixed flow rate nozzle may not be able to provide enough coolant to effectively reduce the temperature and may cause coolant backflow. When the equipment temperature is low, the fixed flow rate may lead to excessive cooling, resulting in energy waste and possible equipment damage. Summary of the Invention

[0003] Purpose of the invention: In order to overcome the shortcomings of the existing technology, this utility model provides a high-precision adjustable anti-backflow spring nozzle, which can adjust the flow rate of coolant sprayed from the nozzle according to the operating status of the production equipment, effectively preventing equipment damage caused by excessively high equipment temperature and waste of coolant when the equipment temperature is too low. At the same time, when the internal air pressure of the liquid delivery device is low, it can actively close the nozzle orifice, thereby preventing the backflow of coolant.

[0004] Technical Solution: To achieve the above objectives, this utility model provides a high-precision adjustable anti-backflow spring nozzle, comprising an annular nozzle, a nozzle valve core coaxially arranged on the inner side of the annular nozzle, forming an annular swirling pressure chamber between the nozzle valve core and the annular nozzle, and an annular spray gap formed between the inner edge of the spray end of the annular nozzle and the outer edge of the nozzle valve core. The water pressure in the swirling pressure chamber can drive the nozzle valve core to move along the axial direction, thereby increasing the width of the annular spray gap; a plurality of swirling channels are arranged in a circumferential array in the wall of the annular nozzle on the side away from the spray end, and the liquid outlet end of each swirling channel is connected to the swirling pressure chamber. The water flow into the swirling pressure chamber from the plurality of swirling channels can drive the liquid in the swirling pressure chamber to form a swirling flow.

[0005] Furthermore, it also includes an elastic component, which applies a spring force to the nozzle valve core through a force transmission structure that is opposite to the spray direction of the annular nozzle, so that the annular spray gap is closed under normal conditions.

[0006] Furthermore, each swirl channel is inclined relative to the axis of the annular nozzle, and the axis of each swirl channel does not intersect with the axis of the annular nozzle.

[0007] Furthermore, it also includes a stroke control cylinder. A sleeve is integrally connected coaxially below the annular nozzle. The upper end of the stroke control cylinder is movably sleeved outside the sleeve. The lower end of the stroke control cylinder is integrally provided with a cone pointing downwards on the same axis. An internal threaded hole is opened at the center of the cone. The force transmission structure includes a force transmission rod. The upper end of the force transmission rod is integrally connected to the lower end of the nozzle valve core. The lower end of the force transmission rod passes coaxially through the force transmission rod through hole in the sleeve and is threaded into the internal threaded hole. An elastic component is provided between the outer wall of the force transmission rod and the inner wall of the stroke control cylinder.

[0008] Furthermore, the elastic component is a compression spring, and the lower end of the compression spring exerts a downward thrust on the cone.

[0009] Furthermore, there is a stroke gap between the upper end of the stroke control cylinder and the lower end of the annular nozzle.

[0010] Beneficial effects: The high-precision adjustable anti-backflow spring nozzle of this utility model can adjust the pressure inside the liquid delivery device according to the operating status of the production equipment, thereby regulating the flow rate of coolant sprayed from the nozzle. It can effectively prevent equipment damage caused by excessively high equipment temperature and coolant waste caused by excessively low equipment temperature. At the same time, when the air pressure inside the liquid delivery device is low, it can actively close the nozzle orifice to prevent the backflow of coolant. Attached Figure Description

[0011] Figure 1 This is a structural cross-sectional view of a high-precision adjustable anti-backflow spring nozzle according to the present invention from the main view perspective;

[0012] Figure 2 This is an application scenario diagram of a high-precision adjustable anti-backflow spring nozzle according to this utility model. Detailed Implementation

[0013] The present invention will be further described below with reference to the accompanying drawings.

[0014] As attached Figure 1 As shown, a high-precision adjustable anti-backflow spring nozzle includes an annular nozzle 1. A nozzle valve core 3 is coaxially arranged on the inner side of the annular nozzle 1, forming an annular swirling pressure chamber 7 between the nozzle valve core 3 and the annular nozzle 1. An annular spray gap 8 is formed between the inner edge of the spray end of the annular nozzle 1 and the outer edge of the nozzle valve core 3. The water pressure in the swirling pressure chamber 7 can drive the nozzle valve core 3 to move along the axial direction, thereby increasing the width of the annular spray gap 8. Several swirling channels 6 are arranged in a circular array in the wall of the annular nozzle 1 on the side away from the spray end. The liquid outlet end of each swirling channel 6 is connected to the swirling pressure chamber 7. The water flow into the swirling pressure chamber 7 from the several swirling channels 6 can drive the liquid in the swirling pressure chamber 7 to form a swirling flow.

[0015] It also includes an elastic component, which applies a spring force to the nozzle valve core 3 through a force transmission structure that is opposite to the spray direction of the annular nozzle 1. Thus, under normal conditions, when the force exerted by the liquid in the swirling pressure chamber 7 on the nozzle valve core 3 is less than or equal to the spring force exerted by the elastic component on the nozzle valve core 3, the annular spray gap 8 is in a closed state. When the liquid in the swirling pressure chamber 7 is applied to the nozzle valve core 3 and the force along the spray direction of the annular nozzle 1 is greater than the force exerted by the elastic component and the external force applied to the nozzle valve core 3 and opposite to the spray direction of the annular nozzle 1, the annular spray gap 8 is in a flowing state.

[0016] like Figure 1 As shown, each swirl channel 6 is inclined relative to the axis of the annular nozzle 1, and the axis of each swirl channel 6 does not intersect with the axis of the annular nozzle 1, that is... Figure 1 The axes of the two swirling channels 6 shown are set at an angle to the main viewing plane. In this scheme, the number of swirling channels 6 is generally even. The planes formed by any two symmetrically arranged swirling channels 6 through the axis of the annular nozzle 1 are both the bisecting planes of the annular nozzle 1. The axes of the two symmetrically arranged swirling channels 6 are set at an angle to their corresponding bisecting planes, and the axes of the two symmetrically arranged swirling channels 6 are symmetrical with respect to their corresponding bisecting planes. Generally, the angle formed between each swirling channel 6 and its corresponding bisecting plane is 12°~13°, and each swirling channel 6 is uniformly inclined in a clockwise or counterclockwise direction. This arrangement allows the swirling water to flow into the swirling stream through several swirling channels 6. The water flow in pressure chamber 7 drives the liquid in swirling pressure chamber 7 to form a swirling flow that rotates clockwise or counterclockwise. This increases the force exerted by the liquid in swirling pressure chamber 7 on the nozzle valve core 3, allowing for more precise control of the width of the annular jet slit 8 when changing the internal pressure of the infusion device. The direction of the swirling liquid in swirling pressure chamber 7 is determined by the inclination direction of each swirling channel 6. Simultaneously, spiral grooves are formed along the extension direction on the inner wall of each swirling channel 6. The structure of the spiral grooves further enhances the speed at which the water flow entering swirling pressure chamber 7 through several swirling channels 6 drives the liquid in swirling pressure chamber 7 to form a swirling flow, as well as the intensity of the force exerted by the swirling liquid on the nozzle valve core 3.

[0017] like Figure 2As shown, the annular nozzle 1 is embedded in the outlet end of the coolant pipe 13, which connects to the interior of the steam pipe 14. When the steam pipe 14 is filled with hot steam, the steam in the steam pipe 14 exerts pressure on the top of the nozzle valve core 3 in the opposite direction to the spray direction of the annular nozzle 1. The elastic component applies a spring force to the nozzle valve core 3 in the opposite direction to the spray direction of the annular nozzle 1 through the force transmission structure. If coolant needs to be sprayed into the steam pipe 14 at this time, the force exerted by the coolant in the swirling pressure chamber 7 on the nozzle valve core 3 in the spray direction of the annular nozzle 1 needs to exceed the force exerted by the elastic component and the hot steam in the steam pipe 14 on the nozzle valve core 3. Therefore, it is necessary to increase the flow rate of the coolant in the coolant pipe 13, thereby increasing the pressure in the coolant pipe 13 and making the coolant in the coolant pipe 13... The force applied to the nozzle valve core 3 increases until the annular injection slit 8 opens. In this state, the coolant in the coolant pipe 13 is injected into the steam pipe 14 through the annular injection slit 8 to form a conical coolant jet. As the liquid in the swirling pressure chamber 7 forms a swirling flow under the action of the water flow entering through several swirling channels 6, the conical coolant jet is also in a swirling state. Under the combined action of the entrainment of the hot steam flow in the steam pipe 14 and the rotation of its own swirling state, the conical coolant jet forms a coolant mist and neutralizes the hot steam in the steam pipe 14, thereby reducing the temperature of the hot steam in the steam pipe 14. The spiral groove structure opened on the inner wall of each of the swirling channels 6 along the extension direction can further increase the effect of the conical coolant jet forming a coolant mist.

[0018] It also includes a stroke control cylinder 2. A sleeve 16 is coaxially and integrally connected to the lower part of the annular nozzle 1. The upper end of the stroke control cylinder 2 is movably sleeved outside the sleeve 16. The lower end of the stroke control cylinder 2 is coaxially and integrally provided with a cone 17 with the cone head pointing downwards. An internal threaded hole 12 is opened at the center of the cone 17. The force transmission component includes a force transmission rod 18. The upper end of the force transmission rod 18 is integrally connected to the lower end of the nozzle valve core 3. The lower end of the force transmission rod 18 is provided with an external thread that mates with the internal threaded hole 12. The lower end of the force transmission rod 18 coaxially passes through the force transmission rod through hole 9 inside the sleeve 16 and is threaded into the internal threaded hole. An elastic component is provided between the outer wall of the force transmission rod 18 and the inner wall of the stroke control cylinder 2.

[0019] The annular nozzle 1 has a sliding fit hole 11, and the internal threaded hole 12 is coaxially arranged with the sliding fit hole 11. The lower end of the nozzle valve core 3 has an external thread that mates with the internal threaded hole 12. The lower end of the nozzle valve core 3 passes through the sliding fit hole 11 and the force transmission rod through hole 9 and is threaded into the internal threaded hole 12. The conical surface at the lower end of the cone 17 has a guiding function, which allows the coolant in the coolant pipe 13 to flow more quickly through each swirling channel 6 into the swirling pressure chamber 7. When the pressure in the swirling pressure chamber 7 changes, the degree of compression of the elastic component changes accordingly, thereby changing the length of the elastic component. When the pressure in the swirling pressure chamber 7 increases, and the force exerted by the liquid in the swirling pressure chamber 7 on the nozzle valve core 3 is greater than the reaction force of the elastic component and the external force on the nozzle valve core 3, the length of the elastic component shortens, and the liquid in the swirling pressure chamber 7... The force applied to the nozzle valve core 3 along the spray direction of the annular nozzle 1 causes the lower end of the nozzle valve core 3 to move upward along the axial direction relative to the annular nozzle 1 through the engagement between the external thread and the internal thread hole 12, thereby putting the annular spray gap 8 in a flowing state. When the pressure in the swirling pressure chamber 7 decreases and the force exerted by the liquid in the swirling pressure chamber 7 on the nozzle valve core 3 is less than the opposing force of the elastic component and the external force on the nozzle valve core 3, the length of the elastic component increases. The force exerted by the elastic component on the stroke control cylinder 2 in the opposite direction to the spray direction of the annular nozzle 1 causes the stroke control cylinder 2 to move downward along the axial direction relative to the annular nozzle 1 through the engagement between the external thread and the internal thread hole 12, until the annular spray gap 8 is in a closed state.

[0020] The elastic component is a compression spring 5, or other elastic devices. The lower end of the compression spring 5 exerts a downward thrust on the cone 17. The internal space formed between the lower end of the sleeve 16 and the inner wall of the stroke control cylinder 2 is an adjustment cavity 10. The compression spring 5 is disposed in the adjustment cavity 10, and the longest length of the compression spring 5 is less than the length of the stroke control cylinder 2. One end of the compression spring 5 is connected to the upper surface of the cone 17, and the other end abuts against the end face of the lower end of the sleeve 16, thereby making the assembly process more convenient. Under normal conditions, the compression spring 5 is in a compressed state. When the pressure in the swirling pressure chamber 7 changes, the compression spring 5 can transmit force. The threaded engagement between the external thread at the lower end of the rod 18 and the internal threaded hole 12 on the cone 17 allows the stroke control cylinder 2 and the nozzle valve core 3 to move simultaneously relative to the annular nozzle 1 along the axial direction. There is a stroke gap 15 between the upper end of the stroke control cylinder 2 and the lower end of the annular nozzle 1. When the stroke control cylinder 2 moves upward along the axial direction to the maximum stroke, the upper end of the stroke control cylinder 2 abuts against the lower side of the annular nozzle 1. At this time, the width of the annular spray gap 8 is at its maximum value. By changing the width of the stroke gap 15, the maximum opening degree of the annular spray gap 8 can be adjusted, thereby achieving the purpose of adjusting the maximum spray flow of the annular nozzle 1.

[0021] Although the force transmission between the stroke control cylinder 2 and the nozzle valve core 3 can be achieved through the engagement between the internal threaded hole 12 on the cone 17 and the external thread at the lower end of the force transmission rod 18, relying on the threaded structure for force transmission over a long period of time will cause the threaded engagement between the internal threaded hole 12 and the external thread to loosen. More seriously, it will cause damage to the internal threaded hole or the external thread structure, resulting in the nozzle valve core 3 and the force transmission rod 18 disengaging from the stroke control cylinder 2, thus rendering the nozzle unusable. Therefore, a more reliable structure is needed to complete the force transmission between the stroke control cylinder 2 and the nozzle valve core 3.

[0022] It also includes a connecting pin 4, which is a cylindrical pin. The cone 17 has an outer pin hole that mates with the connecting pin 4, and the lower end of the force transmission rod 18 has an inner pin hole that mates with the connecting pin 4. The outer diameter of the connecting pin 4 is equal to the diameter of both the outer and inner pin holes. In the assembled state, the inner and outer pin holes together form a connecting pin locking channel, through which the connecting pin 4 passes and is locked. The inner pin hole extends through the area at the lower end of the force transmission rod 18 where an external thread is provided, and the shaft diameter of the inner pin hole is perpendicular to the shaft diameter of the force transmission rod 18. The outer pin hole extends through the cone 17 and is located within the internal thread hole 1 on the cone 17. Within the area where 2 is located, and the shaft diameter of the outer pin hole is perpendicular to the axis of the cone 17; during the threaded engagement between the external thread at the lower end of the force transmission rod 18 and the internal thread hole 12 on the cone 17, when the axes of the inner pin hole and the outer pin hole are on the same straight line, the inner pin hole and the outer pin hole together form a connecting pin locking channel. At this time, one end of the connecting pin 4 is pushed through one end of the outer pin hole to the other end of the outer pin hole, so that the connecting pin 4 passes through and is locked in the connecting pin locking channel. In this way, the force transmission rod 18 and the cone 17 can be connected together, so that the force transmission between the stroke control cylinder 2 and the nozzle valve core 3 can be completed through the connecting pin 4.

[0023] The working principle of a high-precision adjustable anti-backflow spring nozzle: When the force exerted by the coolant in the swirling pressure chamber 7 on the nozzle valve core 3 in the direction of spraying along the annular nozzle 1 exceeds the force exerted by the compression spring 5 and the hot steam in the steam pipe 14 on the nozzle valve core 3 in the opposite direction of spraying along the annular nozzle 1, the lower end of the nozzle valve core 3, through the cooperation between the connecting pin 4 and the outer pin hole on the stroke control cylinder 2, drives the stroke control cylinder 2 and the nozzle valve core 3 to move upward along the axial direction relative to the annular nozzle 1 simultaneously, thereby putting the annular spray gap 8 into a flow state. According to different working conditions, the width of the annular spray gap 8 can be adjusted by adjusting the magnitude of the force exerted by the coolant in the swirling pressure chamber 7 on the nozzle valve core 3 in the direction of spraying along the annular nozzle 1, thus ensuring that the flow rate of coolant sprayed from the annular spray gap 8 is just right. To meet the cooling requirements under this working scenario; when the force of the coolant in the swirling pressure chamber 7 acting on the nozzle valve core 3 in the direction of spraying along the annular nozzle 1 is less than the force of the compression spring 5 and the hot steam in the steam pipe 14 acting on the nozzle valve core 3 in the opposite direction of spraying along the annular nozzle 1, the force applied by the compression spring 5 to the stroke control cylinder 2 in the opposite direction of spraying along the annular nozzle 1 causes the stroke control cylinder 2 to move downward along the axial direction relative to the annular nozzle 1 through the cooperation between the connecting pin and the inner pin hole at the lower end of the nozzle valve core 3, until the annular spray gap 8 is closed. This can avoid the situation where the coolant flows backward under the pressure of the steam pipe 14 due to the lower pressure in the coolant pipe 13 and the higher pressure in the steam pipe 14, thus improving the overall safety and reliability of the equipment.

[0024] The above are the preferred embodiments described in this utility model. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the principle of this utility model, and these improvements and modifications should also be considered within the scope of protection of this utility model.

Claims

1. A high-precision adjustable anti-backflow spring nozzle, characterized in that: The device includes an annular nozzle (1), with a nozzle valve core (3) coaxially arranged on the inner side of the annular nozzle. An annular swirling pressure chamber (7) is formed between the nozzle valve core (3) and the annular nozzle (1). An annular spray gap (8) is formed between the inner edge of the spray end of the annular nozzle (1) and the outer edge of the nozzle valve core (3). The water pressure in the swirling pressure chamber (7) can drive the nozzle valve core (3) to move along the axial direction, thereby increasing the width of the annular spray gap (8). Several swirling channels (6) are arranged in a circular array in the wall of the annular nozzle (1) on the side away from the spray end. The liquid outlet end of each swirling channel (6) is connected to the swirling pressure chamber (7). The water flow from the several swirling channels (6) into the swirling pressure chamber (7) can drive the liquid in the swirling pressure chamber (7) to form a swirling flow.

2. The high-precision adjustable anti-backflow spring nozzle according to claim 1, characterized in that: It also includes an elastic component, which applies a spring force to the nozzle valve core (3) through a force transmission structure that is opposite to the spray direction of the annular nozzle (1), so that the annular spray gap (8) is in a closed state under normal conditions.

3. A high-precision adjustable anti-backflow spring nozzle according to claim 2, characterized in that: Each of the swirling channels (6) is inclined relative to the axis of the annular nozzle (1), and the axis of each of the swirling channels (6) does not intersect with the axis of the annular nozzle (1).

4. A high-precision adjustable anti-backflow spring nozzle according to claim 3, characterized in that: It also includes a stroke control cylinder (2), a sleeve (16) is coaxially and integrally connected to the lower part of the annular nozzle (1), the upper end of the stroke control cylinder (2) is movably sleeved outside the sleeve (16), the lower end of the stroke control cylinder (2) is coaxially and integrally provided with a cone (17) with the cone head pointing downwards, and an internal thread hole (12) is opened at the center of the cone (17). The force transmission structure includes a force transmission rod (18), the upper end of the force transmission rod (18) is integrally connected to the lower end of the nozzle valve core (3), the lower end of the force transmission rod (18) coaxially passes through the force transmission rod through hole (9) in the sleeve (16) and is threaded into the internal thread hole (12), and the elastic component is provided between the outer wall of the force transmission rod (18) and the inner wall of the stroke control cylinder (2).

5. A high-precision adjustable anti-backflow spring nozzle according to claim 4, characterized in that: The elastic component is a compression spring (5), and the lower end of the compression spring (5) exerts a downward thrust on the cone (17).

6. A high-precision adjustable anti-backflow spring nozzle according to claim 5, characterized in that: There is a stroke gap (15) between the upper end of the stroke control cylinder (2) and the lower end of the annular nozzle (1).

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