Axial force self-balancing type two-section concentric rotating cleaning nozzle

Abstract

The invention belongs to the technical field of high-pressure water jet cleaning, and discloses an axial force self-balancing type two-section concentric rotating cleaning spray head to solve the problems that in the prior art, a spray head is large in machining difficulty, unbalanced in axial stress, ineffective in rotating action and the like, the spray head comprises a spray nozzle, a shaft core integrally rotating with the spray nozzle is installed on the spray nozzle, and a lining is installed on one side of the shaft core; a connector is installed outside the lining, an axial-to-radial flow channel is arranged in the connector and communicated with a radial drainage hole formed in the lining, the radial drainage hole is communicated with a main flow channel arranged in the shaft core, a first containing cavity is formed between the shaft end of the shaft core and an inner cavity of the connector, and a control protruding shoulder is arranged at the installation position of the shaft core and the lining. The central spindle and the bushing adopt a control shoulder design to form a throttling opening, and the throttling opening can dynamically adjust the opening size according to the axial stress of the central spindle and change the damping effect of the throttling opening, so that the central spindle always stays at an axial force balance position, and the problem that the spinning action of the spray head fails due to the fact that the end face of the central spindle is pressed tightly is solved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of high-pressure water jet cleaning, in particular to an axial force self-balancing two-section concentric rotary cleaning nozzle. BACKGROUND

[0002] The rotary cleaning nozzle is a cleaning device that uses high-pressure water to drive the nozzle to rotate, and is widely used in the fields of pipeline cleaning and exchanger cleaning.

[0003] The high-pressure water-driven self-rotating nozzle on the market mainly adopts a three-section concentric structure with axial water inlet, that is, the coaxiality of three parts, namely the shaft core and the shell, the shaft core and the joint, needs to be ensured. The nozzle of this structure has high processing difficulty and high assembly precision, and the axial flow of high-pressure water will cause the axial force imbalance of the rotating assembly of the nozzle, resulting in problems such as vibration, wear of the sealing element and failure of the rotating action.

[0004] The prior art such as the pipe cleaning rotary nozzle disclosed in patent CN2020229340426 sets a copper core in the central shaft, which avoids the problem of high wear degree of the central shaft under high-speed rotation, but the multiple concentric cooperation between the rotating assembly and the non-rotating assembly requires high processing precision and high cost, and the prior art cannot solve the above technical problems. SUMMARY

[0005] The present application is to solve the technical problems of high processing difficulty, axial force imbalance and rotating action failure in the existing rotary cleaning nozzle, and provides an axial force self-balancing two-section concentric rotary cleaning nozzle.

[0006] In order to achieve the above purpose, the following technical solutions are adopted in the present application:

[0007] An axial force self-balancing two-section concentric rotary cleaning nozzle, comprising a nozzle, a shaft core rotatable with the nozzle being mounted on the nozzle, a bushing mounted on the side of the shaft core away from the nozzle, a joint mounted outside the bushing, an axial-to-radial flow channel provided in the joint, the axial-to-radial flow channel being in communication with a radial flow guide hole provided on the bushing, the radial flow guide hole being in communication with a main flow channel provided in the shaft core through a stepped flow guide hole, a first cavity being provided between the shaft end of the shaft core and the inner cavity of the joint, a control shoulder being provided at the mounting position of the shaft core and the bushing, the control shoulder comprising a first gap section and a second gap section, a throttling opening being provided between the first gap section and the second gap section, the size of the throttling opening being dynamically adjustable, and a second cavity being provided on the side of the second gap section away from the throttling opening.

[0008] Further, when the width X of the throttling opening is 0, the width L1 of the second cavity is greater than 2mm. b

[0009] ​Furthermore, the side of the shaft core with the stepped drainage hole is clearance-fitted with the bushing mounting point, and the clearance between the two is 10μm-25μm.

[0010] Furthermore, the gap height between the first gap section and the second gap section is 200μm-500μm.

[0011] Furthermore, the control shoulder is located on the side near the nozzle at the clearance fit between the shaft and the bushing.

[0012] Furthermore, the control shoulder is set on both sides of the clearance fit between the shaft core and the bushing.

[0013] Furthermore, the end of the connector away from the shaft core is provided with a water inlet for connecting a water pipe. The axial to radial flow channel includes a central flow channel that communicates with the water inlet. The central flow channel is provided with a number of radial holes evenly distributed along the circumference. The radial holes communicate with the axial holes provided inside the connector. The axial holes communicate with the radial drainage holes.

[0014] Furthermore, the connector is provided with several oblique holes evenly distributed on it. One end of the oblique hole passes through the shell of the connector, and the other end of the oblique hole communicates with the first cavity.

[0015] Furthermore, the axial hole and the radial drainage hole are connected through a cavity provided between the joint and the bushing.

[0016] Furthermore, the bushing and the connector are connected by threads, and a combined seal is installed at the connection; the nozzle and the shaft are connected by threads.

[0017] Compared with the prior art, the present invention has the following advantages:

[0018] This invention incorporates an axial force self-balancing design, where the nozzle and shaft rotate as a single unit during operation. The shaft and bushing feature a control shoulder design, forming a throttling orifice. This orifice dynamically adjusts its size based on the axial force on the shaft, altering its damping effect and consequently adjusting the pressure in the second cavity. This ensures the shaft remains in an axial force balance position, preventing nozzle self-rotation failure caused by shaft end face compression.

[0019] This invention features a radial water inlet channel design. By setting an axial-to-radial flow channel within the connector and opening a radial drainage hole within the bushing, the axial water inlet is changed to radial water inlet, avoiding the axial impact caused by axial water inlet and effectively eliminating the axial unbalanced force caused by axial water inlet.

[0020] The shaft and bushing of the present invention form two concentric fits in the axial fit (the first gap section and the fit gap), which greatly reduces the processing difficulty, simplifies the processing process, reduces processing errors and installation errors, and alleviates problems such as radial jamming of the rotating component shaft.

[0021] The present invention adopts a non-contact design between the end face of the shaft core and the end face of the connector, eliminating the end face friction pair and eliminating the end face friction jamming between the shaft core and the connector.

[0022] In this invention, a liquid bearing is used between the rotating component shaft and the non-rotating component bushing. By introducing high-pressure liquid from the nozzle into the gap between the shaft and the bushing, a high-pressure liquid film is formed, thus functioning as a liquid bearing.

[0023] When the nozzle of this invention is working, the positive pressure on the thread at the connection between the bushing and the connector keeps the thread in a compressed state, which can effectively prevent the thread from loosening due to vibration during use.

[0024] The bushing and the shaft core of this invention form an end face fit through a controlled shoulder-type connection (first gap section, second gap section and throttling port). This end face fit can both limit the axial movement of the shaft core and achieve static pressure balance adjustment.

[0025] The connector of this invention has a triple function: connecting to the water inlet pipe, radial drainage, and pressure relief. The threaded water inlet interface at the end of the connector connects to the water inlet pipe; the combination of radial and axial holes inside the connector changes the axial liquid inlet at the connector inlet to radial liquid inlet in the main flow channel, alleviating the axial force imbalance caused by axial liquid inlet in the main flow channel; the oblique hole of the connector relieves pressure in the first cavity, ensuring that the end of the shaft near the connector is not subjected to axial force. The connector does not require high-precision fitting and can be manufactured by casting.

[0026] This invention is easy to process, has reliable self-spinning action, is not easy to detach from the joint, has high cleaning efficiency, and is safe and reliable during operation. Attached Figure Description

[0027] Figure 1 This is a schematic diagram of the structure of Embodiment 1 of the present invention.

[0028] Figure 2 This is a schematic diagram of the connector structure of the present invention.

[0029] Figure 3 for Figure 2 The left view.

[0030] Figure 4 for Figure 2 AA sectional view.

[0031] Figure 5 for Figure 3 BB cross-sectional view.

[0032] Figure 6 This is a schematic diagram of the bushing structure of the present invention.

[0033] Figure 7 For the present invention Figure 1A magnified view of a portion of the image.

[0034] Figure 8 This is a schematic diagram of the structure of Embodiment 2 of the present invention.

[0035] The meanings of the reference numerals in the attached drawings are as follows: 1. Nozzle; 2. Shaft core; 21. Main flow channel; 22. Stepped drainage hole; 3. Bushing; 31. Radial drainage hole; 4. Combined seal; 5. Connector; 51. Axial hole; 52. Radial hole; 53. Angled hole; 54. Central flow channel; 55. Water inlet interface; 6. First cavity; 7. Second cavity; 8. Cavity; 9. Fitting clearance; a. First clearance section; b. Throttling port; c. Second clearance section. Detailed Implementation

[0036] The present invention will be further described below with reference to the accompanying drawings and specific embodiments.

[0037] Example 1:

[0038] like Figures 1-7 As shown, an axial force self-balancing two-section concentric rotating cleaning nozzle includes a nozzle 1, which is threadedly connected to a shaft core 2, and the two rotate as a single unit. A bushing 3 is installed on the side of the shaft core 2 away from the nozzle 1. A connector 5 is threadedly connected to the outside of the bushing 3, and the connection between the two is sealed by a combined seal 4 to prevent high-pressure water from leaking from the gap between the bushing 3 and the connector 5, thus affecting the working pressure of the nozzle. The connector 5 is provided with an axial to radial flow channel. The end of the connector 5 away from the shaft core 2 is provided with a water inlet 55 for connecting a water pipe. The axial to radial flow channel includes a central flow channel 54 communicating with the water inlet 55. The central flow channel 54 is provided with a plurality of radial holes 52 evenly distributed along the circumference. The radial holes 52 communicate with axial holes 51 provided inside the connector 5. The axial holes 51 communicate with radial drainage holes 31 provided on the bushing 3 through a cavity 8 provided between the connector 5 and the bushing 3. The radial drainage holes 31 communicate with the main flow channel 21 provided inside the shaft core 2 through stepped drainage holes 22.

[0039] A first cavity 6 is provided between the shaft end of the shaft core 2 and the inner cavity of the connector 5. Several oblique holes 53 are evenly distributed on the connector 5. One end of the oblique hole 53 passes through the shell of the connector 5 and is connected to the outside. The other end of the oblique hole 53 is connected to the first cavity 6.

[0040] A control shoulder is provided at the mounting point of the shaft core 2 and bushing 3. The control shoulder is located on the side of the shaft core 2 and bushing 3 near the nozzle 1 at the clearance fit. The control shoulder includes a first clearance section a and a second clearance section c at the mounting point of the shaft core 2 and bushing 3, and a throttling orifice b is provided between the first clearance section a and the second clearance section c. The side of the second clearance section c away from the throttling orifice b is connected to a second cavity 7. The size of the throttling orifice b can be dynamically adjusted. One end of the shaft core with a stepped drainage hole 22 is clearance fitted to the mounting point of the bushing 3, and the clearance height of the two is 10μm-25μm. The first clearance section a and the second clearance section c are mainly responsible for guiding the fit and have no damping effect. Therefore, the clearance height of the first clearance section a and the second clearance section c is 200μm-500μm. The side of the second cavity 7 away from the second clearance section c is the fitting clearance 9, and the side of the first clearance section a away from the throttling orifice b is the end face of the bushing 3.

[0041] To ensure a tight seal between the shaft core 2 and the bushing 3, the coaxiality tolerance between the shaft core 2 and the bushing 3 must be ≤0.02mm. The outer surface of the shaft core 2 and the inner surface of the bushing 3 form a relative rotating pair with two concentric fits: the first gap section a and the fit gap 9 are concentric fits. The nozzle 1 of this invention has 7 spray holes: forward spray holes, which cause the jet to impact the surface of the object to be cleaned at a certain angle, producing shear and tensile damage to the cleaned surface and improving cleaning efficiency; radial and backward spray holes are eccentric spray holes, which use the recoil force of the high-pressure jet and the eccentricity to generate a rotational driving torque, driving the nozzle rotation assembly, i.e., the nozzle 1 and the shaft core 2, to achieve self-rotation, and can also play the role of expanding the hole and cleaning drill cuttings.

[0042] When the nozzle is working: Connector 5 connects to the high-pressure water inlet pipe. High-pressure water flows through the axial to radial flow channel inside the connector to the cavity 8 formed by connector 5 and bushing 3. It then flows through the radial drainage hole 31 of bushing 3 into the stepped drainage hole 22, and then into the main flow channel 21 to supply liquid to nozzle 1. Finally, it is jetted outward through the nozzle orifice of nozzle 1. Due to the eccentricity of the rearward and lateral spray holes of nozzle 1, a rotational torque is generated, which drives the nozzle rotating assembly, i.e., nozzle 1 and shaft 2, to rotate, performing swirling spray cleaning.

[0043] In this invention, the pressure of the main channel 21 of the nozzle is the working pressure of the nozzle. This pressure is mainly established by the damping effect of the nozzle orifice and the fitting gap 9, wherein the orifice diameter of the nozzle orifice is 0.5mm-0.6mm.

[0044] In this invention, the throttle orifice b forms an adjustable damping, and the width X of the throttle orifice b b When the value is 0, the width L1 of the second cavity 7 should be greater than 2mm. That is, when the throttling port b is closed, it must be ensured that the second cavity 7 cannot be closed, otherwise the static pressure balance design will fail.

[0045] Example 2:

[0046] like Figure 8 As shown, the nozzle structure is the same as that of Embodiment 1, except that the control shoulder is set on both sides of the gap between the shaft core 2 and the bushing 3 (in this embodiment, the control shoulder on the side closer to the nozzle 1 is the same as that in Embodiment 1, and in the control shoulder on the other side, the side of the first gap section a away from the throttle port b is the fitting gap 9, and the side of the second cavity 7 away from the second gap section c is the fitting gap 9).

[0047] In this embodiment, locally adjustable damping can be formed on both sides of the clearance fit between the shaft core 2 and the bushing 3, making the pressure adjustment process more sensitive.

[0048] The static pressure balance adjustment process of this invention is as follows:

[0049] Step 1: The initial position of the nozzle operation is taken as the extreme position where the shaft core 2 extends forward to its farthest point. At this time, the initial opening of the throttling orifice b is 0. When the nozzle starts, because the throttling orifice b is in the closed state, the pressure in the second cavity 7 increases sharply, causing the rotating component shaft core 2 to be subjected to an increased axial force in the rear.

[0050] Step 2: When the axial force on the shaft core 2 is greater than the axial force on the front, the shaft core 2 moves backward, the opening of the throttle port b increases, the damping effect of the throttle port b decreases, and the pressure in the second cavity 7 begins to decrease.

[0051] Step 3: As the pressure in the second cavity 7 decreases, when the axial force on the shaft core 2 is less than the axial force on the front, the shaft core 2 moves forward, the opening of the throttle port b decreases, the damping effect of the throttle port b increases, and the pressure in the second cavity 7 begins to increase again.

[0052] Step 4: Repeat this adjustment until the axial resultant force of shaft core 2 approaches 0. At this point, shaft core 2 will no longer displace and will remain at the force balance position, thus achieving static pressure balance adjustment.

Claims

1. An axial force self-balancing two-section concentric rotating cleaning nozzle, comprising a nozzle (1), wherein a shaft (2) is mounted on the nozzle (1) and rotates integrally with the nozzle (1), characterized in that: The shaft core (2) is fitted with a bushing (3) on the side away from the nozzle (1). A connector (5) is fitted on the outside of the bushing (3). An axial to radial flow channel is provided inside the connector (5). The axial to radial flow channel is connected to a radial drainage hole (31) provided on the bushing (3). The radial drainage hole (31) is connected to the main flow channel (21) provided in the shaft core (2) through a stepped drainage hole (22). A first cavity (6) is provided between the shaft end of the shaft core (2) and the inner cavity of the connector (5). A control shoulder is provided at the installation point of the shaft core (2) and the bushing (3). The control shoulder includes a first gap section (a) and a second gap section (c). A throttling orifice (b) is provided between the first gap section (a) and the second gap section (c). The size of the throttling orifice (b) can be dynamically adjusted. A second cavity (7) is provided on the side of the second gap section (c) away from the throttling orifice (b).

2. The axial force self-balancing two-section concentric rotating cleaning nozzle according to claim 1, characterized in that: The width X of the throttle orifice (b) b When the value is 0, the width L1 of the second cavity (7) is greater than 2mm.

3. The axial force self-balancing two-section concentric rotating cleaning nozzle according to claim 2, characterized in that: The side of the shaft core (2) with the stepped drainage hole (22) is fitted with the bushing (3) with a clearance fit, and the fit gap between the two is 10μm-25μm.

4. The axial force self-balancing two-section concentric rotating cleaning nozzle according to claim 3, characterized in that: The gap height between the first gap segment (a) and the second gap segment (c) is 200μm-500μm.

5. The axial force self-balancing two-section concentric rotating cleaning nozzle according to claim 4, characterized in that: The control shoulder is located on the side of the shaft core (2) and bushing (3) near the nozzle (1) at the gap fit.

6. The axial force self-balancing two-section concentric rotating cleaning nozzle according to claim 4, characterized in that: The control shoulder is located on both sides of the clearance fit between the shaft core (2) and the bushing (3).

7. An axial force self-balancing two-section concentric rotating cleaning nozzle according to claim 5 or 6, characterized in that: The connector (5) is provided with a water inlet (55) for connecting a water pipe at one end away from the shaft core (2). The axial to radial flow channel includes a central flow channel (54) connected to the water inlet (55). The central flow channel (54) is provided with a plurality of radial holes (52) evenly distributed along the circumferential direction. The radial holes (52) are connected to the axial holes (51) provided inside the connector (5). The axial holes (51) are connected to the radial drainage holes (31).

8. The axial force self-balancing two-section concentric rotating cleaning nozzle according to claim 7, characterized in that: The connector (5) is provided with several oblique holes (53) evenly distributed on it. One end of the oblique hole (53) passes through the shell of the connector (5), and the other end of the oblique hole (53) is connected to the first cavity (6).

9. The axial force self-balancing two-section concentric rotating cleaning nozzle according to claim 8, characterized in that: The axial hole (51) and the radial drainage hole (31) are connected through a cavity (8) provided between the connector (5) and the bushing (3).

10. The axial force self-balancing two-section concentric rotating cleaning nozzle according to claim 1, characterized in that: The bushing (3) and the connector (5) are connected by threads, and a combined seal (4) is installed at the connection; the nozzle (1) and the shaft (2) are connected by threads.

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