CN220134090U - Hydraulic vortex brake device - Google Patents

Abstract

The utility model provides a hydraulic vortex brake device, which comprises a plurality of through holes or grooves arranged on the high pressure side of a static pair of a bushing; the liquid flows through the gap between the rotating shaft sleeve moving pair and the lining static pair, forms vortex at the through hole or the groove, counteracts the velocity component of the liquid flow in the circumferential direction and reduces the velocity component in the axial direction. The utility model can effectively improve the running stability of the multistage long-shaft rotary power pump or hydraulic turbine rotor, greatly reduce the rotor frequency amplitude and vibration speed performance index, and improve the critical rotation speed of the rotor to avoid resonance.

Description

Hydraulic vortex brake device

Technical Field

The utility model relates to the technical fields of rotary power centrifugal pumps, hydraulic turbines and the like, in particular to a hydraulic vortex brake device.

Background

The rotary power centrifugal pump, hydraulic turbine and other equipment are usually provided with a dynamic and static pair matched with a shaft sleeve dynamic pair and a lining static pair which play a role in throttling and pressure saving at the stator and rotor positions. The dynamic and static structure solves the throttling problem of high and low pressure, but increases the length of the rotor and reduces the rigidity of the rotor; meanwhile, the cross coupling of the rotor is aggravated by uneven liquid film pressure distribution caused by uneven gaps between the dynamic and static pairs due to processing and assembly errors.

The rotary power centrifugal pump, hydraulic turbine and other equipment are usually provided with a dynamic and static pair matched with a shaft sleeve dynamic pair and a lining static pair which play a role in throttling and pressure saving at the stator and rotor positions. The dynamic and static structures are designed with small gaps and long strokes, and sometimes are matched with a plurality of annular grooves and spiral grooves to improve the throttling and depressurization effect, and the structures are all based on the principle of local resistance loss in fluid mechanics, so that the local resistance coefficient is improved, and the purposes of depressurization and throttling are achieved.

However, in these structures (as shown in fig. 1 to 3), the gap distribution is uneven due to the pre-rotation of the medium when the rotating member rotates and the gap is entered, the liquid film between the dynamic and static pairs is disturbed, the formed liquid film supporting force is irregularly changed, and the rigidity and the running stability of the rotor are affected.

As shown in FIG. 4, the radial clearance 3 ' between the bush static pair 1 ', the sleeve dynamic pair 2 ', the bush static pair 1 ' and the sleeve dynamic pair 2 '. When the shaft sleeve kinematic pair 2 'rotates, peripheral fluid is driven to have higher circumferential velocity, and when entering the gap 3', cross coupling is formed between the peripheral fluid and an axial velocity component, a liquid film is in a disorder state, and irregular fluctuation force is generated on the rotor.

Disclosure of Invention

According to the technical problem, a hydraulic vortex brake device is provided.

The utility model adopts the following technical means:

a hydraulic vortex brake device comprises a plurality of through holes or grooves arranged on the high pressure side of a static pair of a bushing; the liquid flows through the gap between the rotating shaft sleeve moving pair and the lining static pair, forms vortex at the through hole or the groove, counteracts the velocity component of the liquid flow in the circumferential direction and reduces the velocity component in the axial direction.

The through holes are densely distributed on the radial outer wall of the high-pressure side of the bushing static pair and penetrate through the outer wall of the bushing static pair, the through holes are obliquely arranged, the outer ends of the through holes are far away from the high-pressure side of the bushing static pair, and the inner ends of the through holes are close to the high-pressure side of the bushing static pair.

The grooves are densely arranged on the axial side wall of the high-pressure side of the bushing static pair; the grooves are obliquely arranged, and the oblique direction of the grooves is in the same direction with the rotation direction of the shaft sleeve moving pair.

Compared with the prior art, the utility model has the following advantages:

1. the utility model can effectively improve the running stability of the multistage long-shaft rotary power pump or hydraulic turbine rotor, greatly reduce the rotor frequency amplitude and vibration speed performance index, and improve the critical rotation speed of the rotor to avoid resonance.

2. The utility model can effectively compensate the reduction of the rigidity of the rotor caused by the increase of the length of the rotor due to the static pair structure of the bushing, the static pair of the bushing after stabilization becomes a bearing bush effect instead, the rigidity of the rotor is improved, and the static pair of the rotor of the rotary power pump or the hydraulic turbine is replaced by the static pair of the vortex brake bushing with the structure of the utility model, thereby breaking through the limit of the number of stages and realizing the application of more stages.

3. The utility model has higher tolerance degree of processing and assembling errors of the integral parts of the equipment, can reduce the processing precision and assembling precision requirements of other parts of the multistage rotary power pump or the hydraulic turbine, and is beneficial to improving the efficiency and reducing the cost.

For the reasons described above, the present utility model can be widely popularized in the field of pumps and the like.

Drawings

In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are some embodiments of the present utility model, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

Fig. 1 is a front view of a conventional bushing static and secondary in the background of the utility model.

Fig. 2 is a front view of a conventional bushing static pair (shorter) in the background of the utility model.

Fig. 3 is a side view of a conventional bushing in the background of the utility model.

FIG. 4 is a graph showing the flow distribution of a conventional bushing static pair and bushing in cooperation with the prior art according to the present utility model.

Fig. 5 is a front view of a hydraulic vortex brake device in embodiment 1 of the present utility model.

Fig. 6 is a side view (high pressure side) of the hydraulic eddy current brake configuration in embodiment 1 of the utility model.

FIG. 7 is a graph showing the distribution of liquid flow when the static and auxiliary bushings are engaged with the bushing in example 1 of the present utility model.

Fig. 8 is a front view of a hydraulic vortex brake device in embodiment 2 of the present utility model.

Fig. 9 is a side view (high pressure side) of the hydraulic eddy current brake configuration in embodiment 2 of the utility model.

FIG. 10 is a graph showing the flow pattern of the bushing static pair and bushing in example 2 of the present utility model.

Fig. 11 is a partial schematic view of the K-direction of fig. 10.

Detailed Description

It should be noted that, without conflict, the embodiments of the present utility model and features of the embodiments may be combined with each other. The utility model will be described in detail below with reference to the drawings in connection with embodiments.

For the purpose of making the objects, technical solutions and advantages of the embodiments of the present utility model more apparent, the technical solutions of the embodiments of the present utility model will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present utility model, and it is apparent that the described embodiments are only some embodiments of the present utility model, not all embodiments. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the utility model, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the utility model without making any inventive effort, are intended to be within the scope of the utility model.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present utility model. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.

The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present utility model unless it is specifically stated otherwise. Meanwhile, it should be clear that the dimensions of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but are intended to be part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.

In the description of the present utility model, it should be understood that the azimuth or positional relationships indicated by the azimuth terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal", and "top, bottom", etc., are generally based on the azimuth or positional relationships shown in the drawings, merely to facilitate description of the present utility model and simplify the description, and these azimuth terms do not indicate and imply that the apparatus or elements referred to must have a specific azimuth or be constructed and operated in a specific azimuth, and thus should not be construed as limiting the scope of protection of the present utility model: the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.

Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

In addition, the terms "first", "second", etc. are used to define the components, and are only for convenience of distinguishing the corresponding components, and the terms have no special meaning unless otherwise stated, and therefore should not be construed as limiting the scope of the present utility model.

Example 1

As shown in fig. 5 to 7, a hydraulic vortex brake device comprises a plurality of through holes 4 arranged on the high pressure side of a bush static pair 1, wherein the through holes 4 are densely arranged on the radial outer wall of the high pressure side of the bush static pair 1 and penetrate through the outer wall of the bush static pair 1, the through holes 4 are obliquely arranged, the outer ends of the through holes 4 are far away from the high pressure side of the bush static pair 1, and the inner ends of the through holes are close to the high pressure side of the bush static pair 1. When the sleeve moving pair 2 rotates, the pressure in the gap 3 between the sleeve moving pair 2 and the bush static pair 1 is reduced due to the Bernoulli effect, and high-pressure liquid is injected into the gap 3 through the through hole 4. The injected liquid flow and the liquid flow in the axial direction and the circumferential direction are opposite to each other, so that a throttling stopping effect similar to a Tesla valve is formed, and vortex occurs in the cavity at the through hole 4, thereby eliminating the velocity component in the circumferential direction and reducing the axial velocity component. The flow direction in the gap 3 is stable, the flow speed is reduced, a radial bearing bush function is formed, good support is provided for the rotor, and the rigidity and stability of the rotor in a wet state can be effectively improved.

Example 2

As shown in fig. 8 to 11, a hydraulic vortex brake device comprises a plurality of grooves 5 arranged on the high pressure side of a bush static pair 1, wherein the plurality of grooves 5 are tightly arranged on the axial side wall of the high pressure side of the bush static pair 1; the grooves 5 are obliquely arranged, and the oblique direction of the grooves 5 is in the same direction with the rotation direction of the shaft sleeve moving pair 2. When the shaft sleeve kinematic pair 2 rotates, axial liquid flow velocity components generate opposite impact in a plurality of grooves 5 of the circumferential array at the grooves 5 to form vortexes, so that the velocity components in the circumferential direction are eliminated to the greatest extent, and the axial velocity components are reduced. The liquid flow direction in the gap 3 between the shaft sleeve dynamic pair 2 and the bush static pair 1 is stable, the flow speed is reduced, a radial bearing bush function is formed, good support is provided for the rotor, and the rigidity and stability of the rotor in a running wet state can be effectively improved.

Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present utility model, and not for limiting the same; although the utility model has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some or all of the technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit of the utility model.

Claims (3)

1. A hydraulic vortex brake device comprising a plurality of through holes or grooves arranged on the high pressure side of a static pair of bushings; the liquid flows through the gap between the rotating shaft sleeve moving pair and the lining static pair, forms vortex at the through hole or the groove, counteracts the velocity component of the liquid flow in the circumferential direction and reduces the velocity component in the axial direction.

2. The hydraulic vortex brake device according to claim 1 wherein a plurality of the through holes are densely arranged on the radial outer wall of the high pressure side of the bush static pair and penetrate the outer wall of the bush static pair, the through holes are obliquely arranged, the outer ends of the through holes are far away from the high pressure side of the bush static pair, and the inner ends of the through holes are near the high pressure side of the bush static pair.

3. A hydraulic vortex brake device according to claim 1 wherein a plurality of the grooves are densely arranged on the axial side wall of the high pressure side of the bushing static pair; the grooves are obliquely arranged, and the oblique direction of the grooves is in the same direction with the rotation direction of the shaft sleeve moving pair.