WO2021134818A1 - 一种高抗空化性能的诱导轮 - Google Patents

一种高抗空化性能的诱导轮 Download PDF

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Publication number
WO2021134818A1
WO2021134818A1 PCT/CN2020/071060 CN2020071060W WO2021134818A1 WO 2021134818 A1 WO2021134818 A1 WO 2021134818A1 CN 2020071060 W CN2020071060 W CN 2020071060W WO 2021134818 A1 WO2021134818 A1 WO 2021134818A1
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Prior art keywords
inducer
axial flow
flow channel
blade
cavitation
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PCT/CN2020/071060
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English (en)
French (fr)
Inventor
付强
朱荣生
王秀礼
龙云
陈一鸣
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Jiangsu University
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Jiangsu University
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2238—Special flow patterns
    • F04D29/225—Channel wheels, e.g. one blade or one flow channel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps

Definitions

  • the invention relates to the field of fluid machinery, in particular to an inducer with high anti-cavitation performance.
  • Inducer wheels are mostly used in aviation, aerospace, refrigeration and other occasions that require high cavitation.
  • the structural size and quality of the propellant supply system are strictly limited.
  • the propellant pump In order to minimize the size and quality of the structure, the propellant pump needs a higher speed, and in order to reduce the quality and scale of the tank pressurization system, the propellant tank needs a lower pressure. According to the characteristics of high speed and low inlet pressure of the propellant pump in the propellant supply system, the propellant pump is required to have very high anti-cavitation performance.
  • the method of adding an inducer in front of the centrifugal impeller is usually used to improve the anti-cavitation performance of the pump, but the improvement is limited, and when the working conditions deviate from the design point far away, it is limited by the anti-cavitation performance of the inducer itself. Its anti-cavitation performance still does not meet the requirements of normal operation under low inlet pressure. In aerospace jet engines, it is necessary to pressurize and transport extremely low temperature fluids such as liquid hydrogen or liquid oxygen. In order to maintain its suction performance, an inducer is required. In the liquid rocket engine turbo pump, in order to obtain a smaller mass and a larger thrust-to-mass ratio, the inducer in the high-speed inducer centrifugal pump often works under potential cavitation conditions.
  • a foreign patent discloses a design of an inducer used to push high-viscosity fluid into a centrifugal pump.
  • a very close gap is formed between the spiral blade of the inducer and the shell of the inducer, and the spiral blade is configured to allow the fluid to pass through.
  • the pressure is increased to solve the problem of the fluid rotating with the inducer blades.
  • the efficiency of the entire device is not high and cannot meet the needs of some occasions.
  • the work done by the blades of the inducer on the medium is achieved by the lift of the blade profile, and does not rely on centrifugal force at all.
  • the inducer rotates, the blade produces a certain centrifugal force, which causes the medium to produce a radial flow component along the blade.
  • This radial flow makes its anti-cavitation performance worse and the unit performance deteriorates.
  • the larger the geometric size of the inducer the stronger the radial centrifugal force effect, which is also an important factor restricting the inducer to further improve the anti-cavitation performance and enlargement of the inducer. If the above problems are to be solved, it is necessary to eliminate or suppress the centrifugal force and radial flow of the blades.
  • the impeller of a centrifugal pump is designed with double flow channels.
  • the centrifugal impeller uses centrifugal force to do work on the medium to convert kinetic energy into pressure energy.
  • the work of the centrifugal impeller on the medium is realized by the centrifugal force generated by the blades.
  • the setting of dual-channels strengthens the radial flow in the impeller channel, thereby strengthening the centrifugal force of the centrifugal impeller.
  • the setting of the dual-channel impeller reduces the pressure pulsation, weakens the impact of the outflow, and reduces the impact of dynamic and static interference, but it will Increasing the displacement coefficient results in the blockage of the impeller channel of the centrifugal pump and the increase of the flow rate, which leads to the decrease of its anti-cavitation performance.
  • the traditional inducer is a high specific speed impeller. There is only one axial flow channel, and there is no centrifugal force that promotes the separation of liquid and air bubbles. Its external characteristic is that its performance decreases during cavitation. Slow, no obvious sudden decline stage, that is, no serious impact on performance.
  • the characteristic value to measure the cavitation performance of the rust guide wheel is the specific cavitation speed C, as shown in the following formula:
  • the present invention provides an inducer with high anti-cavitation performance, which improves the anti-cavitation performance by increasing the number of multiple axial flow channels.
  • the present invention achieves the above-mentioned technical objects through the following technical means.
  • An inducer with high anti-cavitation performance At least two layers of axial flow passages are arranged on the outer side of the hub of the inducer, and any adjacent axial flow passages are separated by a flow passage partition plate.
  • At least one blade is provided in any of the axial flow passages, and the exit area of any of the axial flow passages is less than or equal to the inlet area.
  • the sweeping and rounding treatment of the inlet edge of the blade has a sweep angle ranging from 10° to 180°, which can further improve the anti-cavitation performance of the induced impeller.
  • the blade is a spiral blade
  • the pitch of the spiral blade is a constant pitch or a variable pitch or a combination of the constant pitch and the variable pitch.
  • the two ends of the flow channel dividing plate are respectively provided with a flow guide structure to prevent the tip leakage and further improve the anti-cavitation performance.
  • the axial flow passage includes an outer axial flow passage and at least one inner axial flow passage; the outer axial flow passage is located on the outer side of the inducer, and at least one layer of the inner axial flow passage is located on the outer side Between the axial flow channel and the hub.
  • the outer radius of the inlet side of the blade is greater than or equal to the outer radius of the outlet side of the blade, and the outer flow line of the outer blade on the outer axial flow channel is equal to the axis line
  • the angle ⁇ is 0° ⁇ 45°.
  • cross-sectional flow area of the inner axial flow channel of each layer decreases according to the increase of the distance to the hub.
  • outer flow line of the outer blade on the outer axial flow channel is provided with an outer rim cover plate to prevent the tip leakage and further improve the anti-cavitation performance.
  • the hub structure of the inducer is a hollow structure.
  • the inducer with high anti-cavitation performance of the present invention has the axial flow channel of the inducer set into a multi-layer axial flow channel, and an additional flow channel partition plate is added between adjacent axial flow channels, which can be effective It suppresses the centrifugal force of the inducer blade and the radial flow in the inducer, thereby improving its anti-cavitation performance.
  • the cross-sectional flow area of the inner axial flow channel of each layer decreases according to the increase of the distance to the hub, so that the degree of twisting of the blade is reduced, so that The blades are designed more reasonably, and are more consistent with the working mechanism of the inducer, which reduces the design error, which has a better effect on restraining the radial effect of the blades on the medium.
  • the multi-layer axial flow channel structure can reduce the flow rate through each axial flow channel and obtain a lower cavitation margin, thereby making the whole induction The anti-cavitation performance of the wheel.
  • the two ends of the flow channel partition plate are respectively provided with a flow guide structure, and the blade inlet edge is swept back and rounded, which can further improve the resistance of the present invention. Cavitation performance.
  • the blade outlet edges in different axial flow channels are arranged at a staggered angle, which can improve the uniformity of the outflow of the inducer.
  • Fig. 1 is a schematic diagram of the structure of a traditional inducer in the prior art.
  • Fig. 2 is an axial projection view of the inducer according to embodiment 1 of the present invention.
  • Fig. 3 is a schematic diagram of the axial flow channel area of the inducer according to the embodiment 1 of the present invention.
  • Fig. 4 is an axial cross-sectional view of the inducer according to Embodiment 1 of the present invention.
  • Fig. 5 is a left side view of Fig. 2.
  • Fig. 6 is an axial projection view of the inducer according to Embodiment 2 of the present invention.
  • FIG. 7 is an axial projection view of the inducer according to Embodiment 3 of the present invention.
  • Example 1 is an inducer with two layers of axial flow channels.
  • the inducer hub 6 is made of the
  • the hub axial flow line 1 is a central area formed by rotating 360° around the axis of the inducer.
  • the outer side of the inducer hub 6 is provided with an axial flow channel A 3 and an axial flow channel B 4 which are not connected to each other, and the axial flow The channel A 3 and the axial flow channel B 4 are separated by a channel separating plate A 2.
  • the axial flow passage A 3 is the inner axial flow passage
  • the axial flow passage B 4 is the outer axial flow passage.
  • the outer axial flow passage is located on the outside of the inducer, and the inner axial flow passage is located on the outer shaft.
  • the included angle ⁇ between the hub axial surface streamline 1 and the axial center line is 0° to 45°, so that the water inlet area can be increased and the flow velocity can be reduced.
  • the water outlet area of the axial flow channel A or the axial flow channel B is smaller than the water inlet area, that is, the water outlet area A 305 is smaller than the water inlet area A 304, and the water outlet area B 405 is smaller than the water inlet area B 404.
  • At least one blade is provided in each axial flow channel. The blades in the same axial flow channel are evenly arranged in the flow channel.
  • the blade inlet side A 301 and the blade inlet side B 401 are swept back and rounded, and the sweep angle ranges from 10° to 180°.
  • the blade 3 is arranged between the outer side of the hub 6 and the inner side of the flow channel dividing plate A 2, and the blade 4 is arranged on the outer side of the flow channel dividing plate A 2.
  • the number of blades in the same axial flow channel is not less than 2, the blades are evenly arranged in the flow channel.
  • the medium on the hub side has accepted the action of the blade in advance and moved to the outer edge, thereby improving the anti-cavitation conditions at the outer edge inlet where cavitation is most likely to occur.
  • the blade inlet edges and blade outlet edges in the different axial flow channels are arranged in a staggered manner, that is, the blade outlet edge A 303 and the axial flow channel B in the axial flow channel A
  • the blade exit side B 403 in the middle is staggered.
  • the blade is a spiral blade, and the pitch of the spiral blade is a constant pitch or a variable pitch or a combination of the constant pitch and the variable pitch.
  • the two ends of the flow channel dividing plate A 2 are respectively provided with a diversion structure, in order to reduce the resistance to the water flow.
  • the diversion structure is a pointed streamline structure.
  • the inner radius R 1 of the blade inlet side A 301 is less than or equal to the inner radius R 3 of the blade outlet side A 303;
  • the outer radius R 2 of the blade inlet side B 401 is greater than or equal to the outer radius R 4 of the blade outlet side B 403;
  • the outer flow line 5 of the outer blade on the axial flow channel B is equal to
  • the included angle ⁇ of the axis line is 0° ⁇ 45°.
  • the cavitation specific speed C value of the axial flow passage is shown in the following formula:
  • the axial flow channel cavitation specific rotation speed C value is shown in the following formula.
  • Embodiment 2 is an inducer with 3 layers of axial flow channels that are not connected to each other.
  • the outer side of the hub 6 of the inducer is provided with an axial flow channel A 3, an axial flow channel B 4, and an axial surface.
  • Flow channel C 8 the axial flow channel A 3 and the axial flow channel C 8 are separated by a flow channel dividing plate B 9, and the axial flow channel B 4 and the axial flow channel C 8 are separated by a flow channel Board A 2 is isolated.
  • the axial flow passage A 3 and the axial flow passage C 8 are both inner axial flow passages, and the axial flow passage B 4 is the outer axial flow passage.
  • the outer axial flow passage is located on the outside of the inducer.
  • the surface flow channel is located between the outer axial surface flow channel and the hub.
  • the blade 3 is arranged between the streamline side 1 of the hub axis and the inner side of the flow channel dividing plate B9, the blade 8 is arranged between the flow channel dividing plate B 9 and the flow channel dividing plate A 2, and the blade 4 is arranged in the flow channel Outside of partition A2.
  • the cross-sectional flow area of the inner axial flow channel of each layer decreases as the distance from the hub increases. It can be seen from the figure that the cross-sectional flow area of the axial flow channel A 3 is larger than the cross-sectional flow area of the axial flow channel C 8.
  • Embodiment 3 is shown in Fig. 7, on the basis of embodiment 1, the outer flow line 5 of the axial flow channel B 4 is provided with an outer rim cover plate 7 to prevent the tip leakage and further improve the anti-cavitation performance.
  • the inducer pressurizes the propellant to generate a certain head to increase the inlet pressure, avoid cavitation, and improve the cavitation performance.
  • its operating conditions often change, especially when the internal partial pressure drops below the saturated vapor pressure and cavitation occurs, which will lead to strong cavitation inside the inducer and cause performance. Decrease and strengthen the vibration of the system structure, thereby affecting the reliability of the entire device system and the service life of the inducer.
  • cavitation margin decreases, cavitation occurs in the vortex and continues to increase, the cavitation zone begins to expand, and the noise increases; as the cavitation margin decreases, the cavitation in the vortex zone separates from the blades and enters the mainstream, leading to The fluid medium in the wheel forms an unsteady jet state, and periodically implicated cavitation appears on the surface of the blade A 302. At this time, the head and power begin to decrease, and the noise and structural vibration are the largest; as the cavitation margin is further reduced, the cavitation The bubble fills the axial flow channel A, and the fluid forms a stable jet state. At this time, the noise and structural vibration quickly drop to the state when no cavitation occurs, and the device head and power drop drastically.
  • the cavitation bubble is closed in the inducer and continues to elongate. Its closure occurs at a position farther and farther downstream from the inducer cascade. After the transition to the separated flow condition, the noise and vibration in the pump decrease sharply, and the inlet The vortex at the location tends to disappear, and the main flow fills the entire flow section.
  • the bubbles generated in the outer flow line 5 are in the axial direction.
  • the bubbles are controlled at a local position on the outer edge, and at the same time, they slowly condense in the multiple flow passages of the inducer and then collapse. There is no blockage of the entire flow passage, which delays the development of cavitation and weakens the effect of cavitation.

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Abstract

一种高抗空化性能的诱导轮，诱导轮轮毂（6）外侧至少设有2层互不连通的轴面流道（3、4），任意相邻的轴面流道（3、4）之间通过流道分隔板（2）隔离。该诱导轮能够提高抗汽蚀性能。

Description

一种高抗空化性能的诱导轮 技术领域
本发明涉及流体机械领域，特别涉及一种高抗空化性能的诱导轮。
背景技术
诱导轮多用于航空、航天、制冷等对空化要求高的场合。在航空、航天领域，由于航空航天飞行器需要在远离地面的高空或太空工作，受飞行器空间尺寸和结构质量的约束，推进剂供应系统的结构尺寸和质量受到严格限制。为了尽量减小结构尺寸和质量，推进剂泵需要较高的转速，而为了减轻贮箱增压系统的质量和规模，推进剂贮箱需要较低的压力。根据推进剂供应系统中的推进剂泵高转速和低入口压力的特点，要求推进剂泵需要具有非常高的抗空化性能。
目前，通常采用在离心叶轮前增设诱导轮的方法提高泵的抗空化性能，但提高幅度有限，而且在偏离设计点较远的工况时，受限于诱导轮自身的抗空化性能，其抗空化性能仍然不满足低入口压力下正常工作的要求。在航天喷气发动机中需要将液态氢或液态氧等极低温流体进行加压输送，为了维持其吸入性能需要设置诱导轮。在液体火箭发动机涡轮泵中，为获得更小的质量、更大的推质比，高速诱导轮离心泵中的诱导轮经常在潜在空化情况下工作。虽然流道内潜在空化情况对泵的稳态输出参数扬程、功率和效率不会产生明显的影响，但会改变系统的动态特性，并在特定条件下引起水力系统压力和流量的自激振荡，严重的空化振荡会降低可靠性，甚至导致破坏。
外国专利公开了一种用于将高粘性流体推入离心泵的诱导轮的设计，通过在诱导轮的螺旋叶片和诱导轮外壳之间形成非常紧密的间隙，并配置螺旋叶片，从而在流体通过装置流向泵时增加压力，来解决流体与诱导轮叶片一起旋转的问题。但是整个装置的效率不高，不能满足某些场合的需求。
外国专利公开了将诱导轮设置成多级，并通过增加诱导轮螺旋面的斜率来改变多级诱导轮的旋向，去除旋转动量，从而降低汽蚀余量。同时，在壳体内壁上设置有与诱导轮旋向相反的螺旋形沟槽，使得涡流在沟槽内流动，而非在叶顶间隙内流动，从而减少流体产生叶顶空化的几率。但该技术在高比转速的场合下性能曲线变得不稳定，这一问题值得商榷。
诱导轮的叶片对介质额做功是依靠叶片型线的升力来实现，完全不依靠离心力。诱导轮在旋转时，叶片产生一定的离心力，导致介质沿叶片产生径向流动分量，这种径向流使得其抗空化性能变差和机组性能下降。在相同流速下，诱导轮的几何尺寸越大，这种径向离心力 作用就越强，这也是制约诱导轮进一步地提高诱导轮的抗空化性能、大型化的重要因素。若要上述问题，就需要消除或抑制叶片的离心力和径向流。
现有技术中存在离心泵的叶轮设计成双流道，离心叶轮利用离心力对介质做功，是将动能转化成压能，离心叶轮对介质的做功是通过叶片产生的离心力来实现的。双流道的设置使得叶轮流道内的径向流动得到了加强，从而加强了离心叶轮的离心力，双流道叶轮的设置减小了压力脉动，削弱了出流冲击，降低动静干涉造成的影响，但会增加排挤系数，造成离心泵叶轮流道堵塞，流速增大，导致其抗空化性能降低。
如图1所示，传统诱导轮是一种高比转速叶轮，只有存在一个轴面流道，不存在促进液体和气泡分离的离心力作用，其外特性的表现是，在空化过程中性能下降缓慢，无明显的突然下降阶段，即对性能无严重影响。衡量锈导轮空化性能的特征值是空化比转速C，如下面公式所示：
Figure PCTCN2020071060-appb-000001
式中：n----诱导轮转速，单位r/min；
Q----通过诱导轮的流量，单位m 3/s；
NPSH R----诱导轮的汽蚀余量，单位m。
从上述公式可知：抗空化性能要求越高，也就是要求NPSH R越低，空化比转速C就越大。由于现有技术水平的限制，采用传统的诱导轮结构，很难大幅度地提高C值。
发明内容
针对现有技术中存在的不足，本发明提供了一种高抗空化性能的诱导轮，通过增加多个轴面流道数量来提高抗空化性能。
本发明是通过以下技术手段实现上述技术目的的。
一种高抗空化性能的诱导轮，所述诱导轮轮毂外侧至少设有2层轴面流道，任意相邻的轴面流道之间通过流道分隔板隔离。
进一步，任意所述轴面流道内至少设有1个叶片，任意所述轴面流道的出口面积小于等于进口面积。
进一步，所述叶片进口边后掠修圆处理，其后掠角取值范围为10°～180°，可以进一步地提高诱导叶轮的抗空化性能。
进一步，所述叶片为螺旋叶片，所述螺旋叶片的螺距为等螺距或变螺距或等螺距与变螺距的组合。
进一步，所述流道分隔板的二端分别设有导流结构，防止叶顶泄漏，进一步提高抗空化性能。
进一步，所述轴面流道包括外侧轴面流道和至少一层内侧轴面流道；所述外侧轴面流道位于诱导轮外侧，至少一层所述内侧轴面流道位于所述外侧轴面流道与轮毂之间。
进一步，在所述外侧轴面流道内，所述叶片进口边的外圆半径大于等于所述叶片出口边的外圆半径，所述外侧轴面流道上外侧叶片的外流线与轴心线的夹角β取0°～45°。
进一步，每层所述内侧轴面流道的横截流通面积根据到轮毂的距离增大而减小。
进一步，所述外侧轴面流道上外侧叶片的外流线设有外轮缘盖板，防止叶顶泄漏，进一步提高抗空化性能。
进一步，所述诱导轮的轮毂结构为空心结构。
本发明的有益效果在于：
1.本发明所述的高抗空化性能的诱导轮，将诱导轮轴面流道设置成多层轴面流道，并在相邻轴面流道之间增设流道分隔板，可有效地抑制诱导轮叶片的离心力，抑制诱导轮中的径向流，从而提高其抗空化性能。
2.本发明所述的高抗空化性能的诱导轮，每层所述内侧轴面流道的横截流通面积根据到轮毂的距离增大而减小，这样叶片的扭曲程度减小，使得叶片得到更合理的设计，并与诱导轮工作机理更吻合，降低了设计误差，这对抑制叶片对介质的径向作用起到较好的效果。
3.本发明所述的高抗空化性能的诱导轮，设置的多层轴面流道结构能降低通过每个轴面流道的流量，获得更低的汽蚀余量，从而使得整个诱导轮的抗空化性能。
4.本发明所述的高抗空化性能的诱导轮，通过流道分隔板的二端分别设有导流结构，且叶片进口边进行后掠修圆，能进一步地提高本发明的抗空化性能。
5.本发明所述的高抗空化性能的诱导轮，不同轴面流道中的叶片出口边错开角度布置，能提高诱导轮出流的均匀性。
附图说明
图1为现有技术中的传统诱导轮结构示意图。
图2为本发明实施例1所述诱导轮的轴面投影图。
图3为本发明实施例1所述诱导轮的轴面流道面积示意图。
图4为本发明实施例1所述诱导轮的轴面剖视图。
图5为图2的左视图。
图6为本发明实施例2所述诱导轮的轴面投影图。
图7为本发明实施例3所述诱导轮的轴面投影图。
图中：
1-轮毂轴面流线；2-流道分隔板A；3-轴面流道A；301-叶片进口边A；302-叶片A；303- 叶片出口边A；304-进水口面积A；305-出水口面积A；4-轴面流道B；401-叶片进口边B；402-叶片B；403-叶片出口边B；404-进口面积B；405-出口面积B；5-外流线；6-轮毂；7-外轮缘盖板；8-轴面流道C；9-流道分隔板B。
具体实施方式
下面结合附图以及具体实施例对本发明作进一步的说明，但本发明的保护范围并不限于此。
实施例1为2层轴面流道的诱导轮，如图2、图3和图5所示，本发明所述的高抗空化性能的诱导轮，所述诱导轮轮毂6是由所述轮毂轴面流线1绕诱导轮轴心线旋转360°所形成的中心区域，所述诱导轮轮毂6外侧设有互不连通的轴面流道A 3和轴面流道B 4，轴面流道A 3和轴面流道B 4之间通过流道分隔板A 2隔离。轴面流道A 3为内侧轴面流道，轴面流道B 4为外侧轴面流道，所述外侧轴面流道位于诱导轮外侧，所述内侧轴面流道位于所述外侧轴面流道与轮毂之间。所述轮毂轴面流线1与轴心线的夹角α取0°～45°，这样可以增大进水口面积，减小流速。所述轴面流道A或轴面流道B的出水口面积比进水口面积小，即出水口面积A 305小于进水口面积A 304，出水口面积B 405小于进水口面积B 404。每个轴面流道中至少设置有一个叶片。所述同一个轴面流道中的叶片被均匀布置在该流道中。为提高抗空化性能，所述叶片进口边A 301和叶片进口边B 401后掠修圆，其后掠角取值范围为10°～180°。叶片3设置在轮毂6外侧和流道分隔板A 2内侧之间，叶片4设置在流道分隔板A 2外侧。所述同一个轴面流道中的叶片数不小于2时，叶片被均匀布置在该流道中。介质进入进口外缘时，轮毂侧的介质已提前接受叶片的作用，并向外缘移动，从而改善了最容易发生空化的外缘进口处的抗空化条件。为提高诱导轮出流的均匀性，不同所述轴面流道内的叶片进口边和叶片出口边分别交错布置，即所述轴面流道A中的叶片出口边A 303与轴面流道B中的叶片出口边B 403错开布置。
如图4所示，所述叶片为螺旋叶片，所述螺旋叶片的螺距为等螺距或变螺距或等螺距与变螺距的组合。所述流道分隔板A 2的二端分别设有导流结构，为减小对水流的阻力。导流结构为尖头的流线型结构。
如图2所示，在所述轴面流道A内，所述叶片进口边A 301的内圆半径R 1小于等于所述叶片出口边A 303的内圆半径R 3；在所述轴面流道B内，所述叶片进口边B 401的外圆半径R 2大于等于所述叶片出口边B 403的外圆半径R 4；所述轴面流道B上外侧叶片的外流线5与轴心线的夹角β取0°～45°。
以2个轴面流道结构的诱导轮为例，其轴面流道空化比转速C值如下面公式所示：
Figure PCTCN2020071060-appb-000002
式中：
n----诱导轮转速，单位r/min；
Q 1----通过轴面流道A的流量，单位m 3/s；
Q 2----通过轴面流道B的流量，单位m 3/s；
NPSH R----诱导轮的汽蚀余量，单位m。
若通过轴面流道A的流量Q 1与轴面流道B的流量Q 2相同，则轴面流道空化比转速C值如下面公式所示。
Figure PCTCN2020071060-appb-000003
相比传统的单个轴面流道，通过每个轴面流道的流量明显降低，在保持同样的C值情况下，可以获得更低的汽蚀余量NPSH R，这也就使得整个诱导轮的空化比转速C值能大幅度地提高。
实施例2为3层互不连通的轴面流道的诱导轮，如图6所示，所述诱导轮的轮毂6外侧设有轴面流道A 3、轴面流道B 4和轴面流道C 8，轴面流道A 3和轴面流道C 8之间通过流道分隔板B 9隔离，轴面流道B 4和轴面流道C 8之间通过流道分隔板A 2隔离。轴面流道A 3和轴面流道C 8均为内侧轴面流道，轴面流道B 4为外侧轴面流道，所述外侧轴面流道位于诱导轮外侧，所述内侧轴面流道位于所述外侧轴面流道与轮毂之间。叶片3设置在轮毂轴面流线侧1和流道分隔板B9内侧之间，叶片8设置在流道分隔板B 9和流道分隔板A 2之间，叶片4设置在流道分隔板A2外侧。每层所述内侧轴面流道的横截流通面积根据到轮毂的距离增大而减小。图中可以看出轴面流道A 3的横截流通面积大于轴面流道C 8的横截流通面积。
实施例3如图7所示，在实施例1的基础上，所述轴面流道B 4的外流线5增加外轮缘盖板7，以防止叶顶泄漏，进一步提高抗空化性能。
在实际运行过程中，诱导轮对推进剂进行加压产生一定扬程以提高入口压力，避免发生空化，从而提高空化性能。然而在诱导轮的高速运转过程中，其运行工况常常会发生变化，尤其是当其内部局部压力降低至饱和蒸气压以下发生空化时，将导致诱导轮内部强烈的空化现象，引起性能下降、系统结构振动加强，从而影响整个装置系统可靠性和诱导轮使用寿命。
以叶片A 302上的空化过程为例，在大汽蚀余量工况下，流场内未出现空化，绕流叶片进口边A 301处的流场出现附面层分离，并形成滞止区；当汽蚀余量和装置的汽蚀余量相等时，在滞止区生成涡流区域。随着汽蚀余量的减少，涡流内产生空化并不断增大，空化区开始扩大，噪声增大；随着空化余量的减小，涡流区空化脱离叶片，进入主流，诱导轮内流体 介质形成非稳定射流状态，在叶片A 302表面出现周期性的牵连形空泡，此时扬程和功率开始下降，噪声和结构振动最大；随着汽蚀余量的进一步减小，空泡充满轴面流道A，流体形成稳定的射流状态，此时噪声和结构振动迅速下降到未发生空化时的状态，装置扬程和功率剧烈下降。空泡在诱导轮中闭合并不断伸长，其闭合发生在距诱导轮叶栅下游越来越远的位置，在过渡到分离绕流工况后，泵内的噪声和振动急剧减小，进口处的漩涡趋于消失，主流充斥在整个过流断面内。
本发明在所述诱导轮轮毂外侧至少设有2层轴面流道，任意相邻的轴面流道之间通过流道分隔板隔离，在外流线5产生的气泡，在沿轴向向前运动的过程中，气泡被控制在外缘局部位置，同时在诱导轮多个流道内缓慢凝结后溃灭，并未产生对整个流道的堵塞，延缓了空化发展的趋势，减弱空化对诱导轮增压能力的影响程度。
所述实施例为本发明的优选的实施方式，但本发明并不限于上述实施方式，在不背离本发明的实质内容的情况下，本领域技术人员能够做出的任何显而易见的改进、替换或变型均属于本发明的保护范围。

Claims (10)

  1. 一种高抗空化性能的诱导轮，其特征在于，所述诱导轮轮毂外侧至少设有2层轴面流道，任意相邻的轴面流道之间通过流道分隔板(2、9)隔离。
  2. 根据权利要求1所述的高抗空化性能的诱导轮，其特征在于，任意所述轴面流道内至少设有1个叶片，任意所述轴面流道的出口面积小于等于进口面积。
  3. 根据权利要求2所述的高抗空化性能的诱导轮，其特征在于，所述叶片进口边后掠修圆处理，其后掠角取值范围为10°～180°。
  4. 根据权利要求2所述的高抗空化性能的诱导轮，其特征在于，所述叶片为螺旋叶片，所述螺旋叶片的螺距为等螺距或变螺距或等螺距与变螺距的组合。
  5. 根据权利要求1所述的高抗空化性能的诱导轮，其特征在于，所述流道分隔板(2、9)的二端分别设有导流结构。
  6. 根据权利要求1-5任一项所述的高抗空化性能的诱导轮，其特征在于，所述轴面流道包括外侧轴面流道和至少一层内侧轴面流道(3、8)；所述外侧轴面流道位于诱导轮外侧，至少一层所述内侧轴面流道(3、8)位于所述外侧轴面流道与轮毂之间。
  7. 根据权利要求6所述的高抗空化性能的诱导轮，其特征在于，在所述外侧轴面流道内，所述叶片进口边的外圆半径大于等于所述叶片出口边的外圆半径；所述外侧轴面流道上外侧叶片的外流线(5)与轴心线的夹角β取0°～45°。
  8. 根据权利要求6所述的高抗空化性能的诱导轮，其特征在于，每层所述内侧轴面流道(3、8)的横截流通面积根据到轮毂的距离增大而减小。
  9. 根据权利要求6所述的高抗空化性能的诱导轮，其特征在于，所述外侧轴面流道上外侧叶片的外流线(5)设有外轮缘盖板(7)。
  10. 根据权利要求9所述的高抗空化性能的诱导轮，其特征在于，所述诱导轮的轮毂(6)结构为空心结构。
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