Axial force self-balancing two-section concentric rotary cleaning nozzle

Abstract

The invention belongs to the technical field of high-pressure water jet cleaning, and discloses an axial force self-balancing two-section concentric rotary cleaning nozzle, to solve the problems of great nozzle machining difficulty, axial force imbalance, rotary action failure and the like in the prior art. The nozzle comprises a nozzle, an axial core which is rotatable integrally with the nozzle is arranged on the nozzle, a bushing is arranged on one side of the axial core, a joint is arranged outside the bushing, an axial-to-radial flow channel is arranged in the joint, the axial-to-radial flow channel is communicated with a radial flow guide hole arranged on the bushing, the radial flow guide hole is communicated with a main flow channel arranged in the axial core, a first cavity is arranged between the shaft end of the axial core and the inner cavity of the joint, a control shoulder is arranged at the mounting position of the axial core and the bushing, the axial core and the bushing are designed with the control shoulder, a throttle port is formed, the throttle port can dynamically adjust the opening size according to the axial force of the axial core, the damping effect of the throttle port is changed, the axial core is always kept at the axial force balance position, and the problem of nozzle self-rotation action failure caused by the end face compression of the axial core is avoided.

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, heat exchanger cleaning, etc.

[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 patent CN2020229340426 discloses a pipeline cleaning rotary nozzle, which sets a copper core in the central shaft, thereby avoiding the problem of high wear degree of the central shaft under high-speed rotation. However, the multiple concentric fittings between the rotating assembly and the non-rotating assembly require 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 present application adopts the following technical solutions:

[0007] An axial force self-balancing two-section concentric rotary cleaning nozzle, comprising a nozzle, a shaft core rotating integrally with the nozzle is mounted on the nozzle, a bushing is mounted on the side of the shaft core away from the nozzle, a joint is mounted outside the bushing, an axial-to-radial flow channel is arranged in the joint, the axial-to-radial flow channel is in communication with a radial flow guide hole arranged on the bushing, the radial flow guide hole is in communication with a main flow channel arranged in the shaft core through a stepped flow guide hole, a first cavity is arranged between the shaft end of the shaft core and the inner cavity of the joint, a control shoulder is arranged at the mounting position of the shaft core and the bushing, the control shoulder comprises a first gap section and a second gap section, a throttling opening is arranged between the first gap section and the second gap section, the size of the throttling opening can be dynamically adjusted, and a second cavity is arranged 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] ​Further, one side of the stepped flow hole of the shaft core is in clearance fit with the mounting position of the bushing, and the fit clearance between the two is 10-25 μm.

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

[0011] Further, the control shoulder is arranged on one side of the clearance fit position of the shaft core and the bushing close to the nozzle.

[0012] Further, the control shoulder is arranged on both sides of the clearance fit position of the shaft core and the bushing.

[0013] Further, the joint is provided with a water inlet interface for connecting a water pipe at the end away from the shaft core, the axial-to-radial flow channel comprises a central flow channel in communication with the water inlet interface, the central flow channel is uniformly arranged with a plurality of radial holes in the circumferential direction, the radial holes are in communication with axial holes arranged in the joint, and the axial holes are in communication with the radial flow holes.

[0014] Further, a plurality of oblique holes are uniformly arranged on the joint, one end of the oblique hole penetrates the shell of the joint, and the other end of the oblique hole is in communication with the first cavity.

[0015] Further, the axial holes and the radial flow holes are in communication through the cavity arranged between the joint and the bushing.

[0016] Further, the bushing and the joint are connected through threads, and a combined sealing element is arranged at the connection position; and the nozzle and the shaft core are connected through threads.

[0017] Compared with the prior art, the present application has the following beneficial effects:

[0018] The present application is designed for axial force self-balancing, the nozzle and the shaft core rotate integrally during the working process of the spray head. The shaft core and the bushing are designed with a control shoulder to form a throttle, the size of the opening of the throttle is dynamically adjusted according to the axial force of the shaft core, the damping effect of the throttle is changed, and then the pressure of the second cavity is adjusted, so that the shaft core always stays at the axial force balance position, and the problem of failure of the self-rotation action of the spray head caused by the end face of the shaft core being pressed tightly is avoided.

[0019] The present application is designed for radial water inlet flow channel, the axial-to-radial flow channel is arranged in the joint, the radial flow hole is arranged in the bushing, the axial water inlet is changed to radial water inlet, the axial impact caused by the axial water inlet is avoided, and the axial unbalanced force caused by the axial water inlet can be effectively eliminated.

[0020] The shaft core and the bushing of the present application only form two concentric fits (the first gap section and the fit clearance position) in the axial fit, which greatly reduces the processing difficulty, simplifies the processing technology, reduces the processing error and the installation error, and relieves the problems such as radial clamping of the shaft core of the rotating assembly.

[0021] The shaft core end face and the joint end face of the application adopt a non-contact design, and there is no end face friction pair, so that end face friction jamming of the shaft core and the joint is eliminated.

[0022] The liquid bearing is used between the shaft core of the rotating assembly and the bushing of the non-rotating assembly in the application. By introducing high-pressure liquid in the nozzle into the gap between the shaft core and the bushing, a high-pressure liquid film is formed to play the role of the liquid bearing.

[0023] When the nozzle works, the positive pressure on the threads at the connection between the bushing and the joint makes the threads in a compressed state, so that the problem of thread loosening caused by vibration during use can be effectively avoided.

[0024] The end face cooperation between the bushing and the shaft core is formed by controlling the convex shoulder type connection (the first gap section, the second gap section and the throttle), and this cooperating end face can not only realize the axial limiting of the shaft core, but also realize the static pressure balance adjustment.

[0025] The joint of the application has the triple effects of connecting the water inlet pipe, radial drainage and pressure relief. The threaded water inlet interface at the end of the joint connects the water inlet pipeline; the combination of the radial hole and the axial hole in the joint can change the axial liquid inlet of the joint inlet to the radial liquid inlet of the main flow channel, which can relieve the phenomenon of axial force imbalance of the main flow channel caused by axial liquid inlet; the inclined hole of the joint can relieve the pressure of the first cavity to ensure that the end of the shaft core close to the joint is not affected by the axial force. The joint has no high-precision cooperation requirement and can be processed by casting.

[0026] The application has low processing difficulty, reliable self-rotation action, high cleaning efficiency, and is safe and reliable during work. BRIEF DESCRIPTION OF DRAWINGS

[0027] Figure 1 It is a structural schematic diagram of embodiment 1 of the application.

[0028] Figure 2 It is a structural schematic diagram of the joint of the application.

[0029] Figure 3 It is Figure 2 the left view.

[0030] Figure 4 It is Figure 2 the A-A sectional view of.

[0031] Figure 5 It is Figure 3 the B-B sectional view of.

[0032] Figure 6 It is a structural schematic diagram of the bushing of the application.

[0033] Figure 7 It is Figure 1a local enlarged schematic view.

[0034] Figure 8 a structural schematic view of embodiment 2 of the present application.

[0035] The meaning of the reference signs is as follows: 1. nozzle; 2. shaft core; 21. main flow channel; 22. stepped flow guide hole; 3. bushing; 31. radial flow guide hole; 4. combined seal; 5. joint; 51. axial hole; 52. radial hole; 53. inclined hole; 54. central flow channel; 55. water inlet interface; 6. first cavity; 7. second cavity; 8. cavity; 9. fit clearance; a. first clearance section; b. throttle; c. second clearance section. DETAILED DESCRIPTION

[0036] The present application will be further described below in conjunction with the drawings and specific embodiments.

[0037] Embodiment 1:

[0038] As Figures 1-7 shown, an axial force self-balancing two-section concentric rotary cleaning nozzle comprises a nozzle 1, the nozzle 1 is threadedly connected with a shaft core 2, and the two are integrally rotated, the shaft core 2 is provided with a bushing 3 on the side away from the nozzle 1, a joint 5 is threadedly connected outside the bushing 3, and the joint 5 is sealed at the connection position with the bushing 3 by a combined seal 4 to prevent high-pressure water from leaking from the gap between the bushing 3 and the joint 5 and affecting the working pressure of the nozzle. The joint 5 is provided with an axial-to-radial flow channel, the joint 5 is provided with a water inlet interface 55 for connecting a water pipe at the end away from the shaft core 2, the axial-to-radial flow channel comprises a central flow channel 54 in communication with the water inlet interface 55, the central flow channel 54 is provided with a plurality of radial holes 52 distributed along the circumferential direction, the radial holes 52 are in communication with axial holes 51 provided inside the joint 5, the axial holes 51 are in communication with radial flow guide holes 31 provided on the bushing 3 through a cavity 8 provided between the joint 5 and the bushing 3, and the radial flow guide holes 31 are in communication with a main flow channel 21 provided inside the shaft core 2 through a stepped flow guide hole 22.

[0039] The shaft core 2 is provided with a first cavity 6 between the shaft end and the inner cavity of the joint 5, the joint 5 is provided with a plurality of inclined holes 53 distributed along the circumferential direction, one end of the inclined holes 53 penetrates the shell of the joint 5 and is in communication with the outside, and the other end of the inclined holes 53 is in communication with the first cavity 6.

[0040] The control shoulder is arranged at the gap fit position of the shaft core 2 and the bushing 3, and is arranged on the side close to the nozzle 1. The control shoulder comprises a first gap section a and a second gap section c arranged at the gap fit position of the shaft core 2 and the bushing 3, and a throttle b is arranged between the first gap section a and the second gap section c. A second cavity 7 is arranged on the side of the second gap section c away from the throttle b. The size of the throttle b can be dynamically adjusted. One end of the stepped flow guide hole 22 of the shaft core is arranged in gap fit with the bushing 3, and the gap height of the gap fit position of the two is 10-25 μm. The first gap section a and the second gap section c are mainly responsible for guiding fit, and have no damping effect, so the gap height of the first gap section a and the second gap section c is 200-500 μm. The side of the second cavity 7 away from the second gap section c is the gap fit position 9, and the side of the first gap section a away from the throttle b is the end face of the bushing 3.

[0041] In order to ensure the gap sealing between the shaft core 2 and the bushing 3, the coaxiality tolerance of the shaft core 2 and the bushing 3 needs to be less than or equal to 0.02 mm. The outer surface of the shaft core 2 and the inner surface of the bushing 3 form a relative rotation pair, and there are two concentric fit positions, i.e. the first gap section a and the gap fit position 9. The nozzle 1 of the present application has seven spray holes: a forward spray hole, a radial spray hole and a backward spray hole. The forward spray hole makes the jet flow impact the surface of the object to be cleaned at a certain angle, and produces shear tensile damage to the surface to be cleaned, thereby improving the cleaning efficiency. The radial spray hole and the backward spray hole are eccentric spray holes, and the rotational driving torque is generated by the action of the high-pressure jet flow back pressure and the eccentric distance, so as to drive the nozzle 1 and the shaft core 2 to rotate.

[0042] When the nozzle works, the joint 5 is connected to the high-pressure water inlet pipe. The high-pressure water flows through the axial-to-radial flow channel in the joint, flows into the cavity 8 formed by the joint 5 and the bushing 3, flows into the stepped flow guide hole 22 through the radial flow guide hole 31 of the bushing 3, and then flows into the main flow channel 21 to supply liquid to the nozzle 1. Finally, the liquid is jetted out through the spray holes of the nozzle 1. Since the backward and lateral spray holes of the nozzle 1 have eccentric distances, the rotational torque is generated, so as to drive the nozzle 1 and the shaft core 2 to rotate and perform rotary spraying cleaning.

[0043] In the present application, the pressure of the main flow channel 21 of the nozzle is the working pressure of the nozzle. The pressure is mainly established by the damping effect of the spray holes of the nozzle and the gap fit position 9. The diameter of the spray holes of the nozzle is 0.5-0.6 mm.

[0044] In the present application, the throttle b forms an adjustable damping, and the width X of the throttle b is less than or equal to 0.5 mm. b When the width X of the throttle b is 0, the width L1 of the second cavity 7 should be greater than 2 mm. That is, when the throttle b is closed, it is necessary to ensure that the second cavity 7 cannot be closed, otherwise the static pressure balance design will fail.

[0045] Example 2:

[0046] As Figure 8 shown, the structure of the spray head is the same as that of Embodiment 1, except that control bosses are arranged on both sides of the gap fit between the shaft core 2 and the bush 3 (in this embodiment, the control boss near the nozzle 1 side is the same as that of Embodiment 1, and in the control boss on the other side, the first gap section a is away from the throttle port b side as the fit gap 9, and the second cavity 7 is away from the second gap section c side as the fit gap 9).

[0047] In this embodiment, partial adjustable damping can be formed on both sides of the gap fit between the shaft core 2 and the bush 3, so that the pressure adjustment process is more sensitive.

[0048] The static pressure balance adjustment process of the present application is as follows:

[0049] Step 1, take the initial position of the spray head work as the shaft core 2 forward to the farthest end of the limit position, at this time the initial opening of the throttle port b is 0. When the spray head is started, because the throttle port b is in the closed state, the pressure of the second cavity 7 rises sharply, causing the shaft core 2 of the rotating assembly to increase the rear axial force.

[0050] Step 2, when the rear axial force of the shaft core 2 is greater than the forward axial force, 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 of the second cavity 7 begins to decrease.

[0051] Step 3, as the pressure of the second cavity 7 decreases, when the rear axial force of the shaft core 2 is less than the forward axial force, 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 of the second cavity 7 begins to increase.

[0052] Step 4, so repeatedly adjust when the shaft core 2 axial force tends to 0, the shaft core 2 no longer displacement, stay in the force balance position, realize static pressure balance adjustment.

Claims

1. A two-section concentric rotary cleaning nozzle with axial force self-balancing, comprising a nozzle (1) and a shaft core (2) rotating with the nozzle (1), characterized in that: The shaft core (2) is provided with a bushing (3) on the side away from the nozzle (1), the bushing (3) is provided with a joint (5) outside, the joint (5) is provided with an axial-to-radial flow channel inside, the axial-to-radial flow channel is communicated with a radial flow guide hole (31) provided on the bushing (3), the radial flow guide hole (31) is communicated with a main flow channel (21) provided in the shaft core (2) through a stepped flow guide hole (22), the side of the shaft core (2) provided with the stepped flow guide hole (22) is in clearance fit with the installation position of the bushing (3), and the fit clearance (9) between the two is 10-25μm, a first cavity (6) is arranged between the shaft end of the shaft core (2) and the inner cavity of the joint (5), a plurality of inclined holes (53) are uniformly arranged on the joint (5), one end of the inclined hole (53) penetrates the shell of the joint (5), the other end of the inclined hole (53) is communicated with the first cavity (6), a control shoulder is arranged at the installation position of the shaft core (2) and the bushing (3), the control shoulder includes a first clearance section (a) and a second clearance section (c), the clearance height of the first clearance section (a) and the second clearance section (c) is 200-500μm, a throttle (b) is arranged between the first clearance section (a) and the second clearance section (c), and the size of the throttle (b) can be dynamically adjusted, a second cavity (7) is arranged on the side of the second clearance section (c) away from the throttle (b), the width X of the throttle (b) is 0, and the width L1 of the second cavity (7) is greater than 2mm. b ​ 2. The axial force self-balancing two-section concentric rotary cleaning nozzle according to claim 1, characterized in that: The control shoulder is arranged at one side of the clearance fit between the shaft core (2) and the bushing (3) close to the nozzle (1).

3. The axial force self-balancing two-section concentric rotary cleaning nozzle according to claim 1, characterized in that: The control shoulder is arranged at both sides of the clearance fit between the shaft core (2) and the bushing (3).

4. The axial force self-balancing two-section concentric rotary cleaning nozzle according to claim 2 or 3, characterized in that: The end of the joint (5) away from the shaft core (2) is provided with a water inlet interface (55) for connecting a water pipe, the axial-to-radial flow channel comprises a central flow channel (54) in communication with the water inlet interface (55), the central flow channel (54) is uniformly arranged with a plurality of radial holes (52) in the circumferential direction, the radial holes (52) are in communication with axial holes (51) arranged in the interior of the joint (5), the axial holes (51) are in communication with the radial drainage holes (31).

5. The axial force self-balancing two-section concentric rotary cleaning nozzle according to claim 4, characterized in that: The axial holes (51) and the radial drainage holes (31) are in communication through a cavity (8) arranged between the joint (5) and the bushing (3).

6. The axial force self-balancing two-section concentric rotary cleaning nozzle according to claim 1, characterized in that: The bushing (3) and the joint (5) are connected through threads, and a combined sealing element (4) is arranged at the connection; the nozzle (1) and the shaft core (2) are connected through threads.

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