A dual-nozzle fluidic pump

Abstract

The application belongs to the technical field of jet pump equipment, and discloses a double-nozzle jet pump capable of improving pumping efficiency. The jet pump comprises a pump body, a sleeve pipe and a pump core. The pump body is provided with a working fluid channel, a transported fluid channel and the pump core. The sleeve pipe is sleeved on the pump body and forms a mixed fluid discharge channel with the sleeve pipe. The pump core comprises an inlet inner cavity connected with the working fluid channel, two nozzles symmetrically connected with the inlet inner cavity along the axial direction, a throat pipe arranged at intervals with the outlet of the nozzle, and a diffusion pipe connected with the outlet of the throat pipe. The diffusion pipe is connected with the mixed fluid discharge channel, and the transported fluid channel is connected with the nozzle. The working fluid enters the inlet inner cavity through the working fluid channel and enters the two nozzles at the same time. A low-pressure area is formed at the outlet of the nozzle, so that the transported fluid is sucked into the nozzle through the transported fluid channel, and then the working fluid and the transported fluid are mixed to form high-speed mixed fluid in the throat pipe. The high-speed mixed fluid is pressurized through the diffusion pipe and discharged through the mixed fluid discharge channel.

Description

Technical Field

[0001] This invention relates to the field of jet pump equipment technology, and specifically to a dual-nozzle jet pump. Background Technology

[0002] Jet pumps, as devices with no moving parts that utilize high-speed fluid entrainment to transport media, are widely used in oil extraction, chemical processes, and mine drainage due to their advantages of simple structure and low maintenance costs. Their core principle follows Bernoulli's equation: the working fluid is accelerated through the nozzle to form a low-pressure zone, entraining the fluid to be transported. The two mix in the throat and then convert kinetic energy into pressure energy for output through the diffuser.

[0003] However, existing jet pumps typically use a single nozzle, which has two inherent drawbacks: 1) The low-pressure zone generated by the single-nozzle structure is limited, resulting in insufficient entrainment capacity for the fluid being transported, leading to low pumping efficiency. Experimental data shows (see Table 1) that the conventional pump achieves a flow rate of only 219.31 m³ / h of suctioned liquid at an operating pressure of 26.5 MPa. 3 The flow rate ratio (suctioned fluid flow rate / working fluid flow rate) is as low as 0.903, which greatly limits the suction efficiency of the jet pump; 2) Severe energy loss in the flow channel: Turbulent impacts are easily generated when the working fluid enters the inlet chamber, resulting in kinetic energy loss. In particular, when attempting to increase the flow rate by increasing the number of nozzles, mutual interference of the flow field will occur, further aggravating energy loss.

[0004] Despite existing technologies attempting to optimize nozzle parameters (such as throat-to-nozzle distance and diffusion angle), existing jet pumps have still failed to overcome the bottleneck in suction efficiency. Summary of the Invention

[0005] To improve suction efficiency, this invention proposes a dual-nozzle jet pump.

[0006] The dual-nozzle jet pump according to the present invention includes: a pump body, wherein a working fluid channel and a conveyed fluid channel are formed within the pump body; a sleeve sleeved outside the pump body, wherein a mixed fluid discharge channel is formed between the pump body and the sleeve; and a pump core disposed within the pump body, the pump core including an inlet cavity communicating with the working fluid channel, nozzles symmetrically connected to both ends of the inlet cavity along the axial direction, throats spaced apart from the outlets of each nozzle, and diffusers communicating with the outlets of each throat, the diffusers communicating with the mixed fluid discharge channel, and the conveyed fluid channel communicating with the nozzles. The working fluid enters the inlet cavity through the working fluid channel and simultaneously enters the nozzles at both ends, forming a low-pressure zone at the nozzle outlets. This causes the conveyed fluid to be drawn into the nozzles through the conveyed fluid channel and merge with the working fluid therein, then enters the throats for thorough mixing to form a high-speed mixed fluid. The high-speed mixed fluid is pressurized by the diffuser and discharged through the mixed fluid discharge channel.

[0007] Furthermore, the inlet cavity includes a constant diameter section and tapered sections symmetrically connected to both ends of the constant diameter section, the tapered sections having an inner diameter that gradually decreases in the direction from the constant diameter section toward the nozzle.

[0008] Furthermore, the inlet cavity is symmetrically provided with inlet cavity channels on both sides, and the inlet cavity channels are connected to the working fluid channels.

[0009] Furthermore, the nozzle outlet diameter d ≤ 3.5 mm and the inlet diameter is 1.25 d ~ 1.3 d.

[0010] Furthermore, the distance between the nozzle outlet and the throat inlet is 1.2d to 1.35d.

[0011] Furthermore, the ratio of the inner surface area of ​​the throat to the inner surface area of ​​the nozzle is 3.5 to 4.

[0012] Furthermore, the length of the larynx is 6 to 8 times the inner diameter of the larynx.

[0013] Furthermore, the diffuser is a single-angle diffuser with a diffusion angle of 5–8°.

[0014] Furthermore, the length of the diffuser tube is not less than four times the inner diameter of the throat tube.

[0015] Furthermore, the inlet cavity, nozzle, throat, and diffuser are arranged coaxially.

[0016] Compared with existing technologies, the dual-nozzle jet pump of this invention, through its unique dual-nozzle structure and optimized design of the dimensions, shapes, spacing, and arrangement of components such as the inlet cavity, nozzles, throat, and diffuser, can effectively increase the flow rate of the transported fluid while maintaining the same working fluid flow rate, thereby significantly improving the pump's delivery efficiency. Simultaneously, the enhanced sealing treatment of each component, the application of high-pressure resistant materials, and the coaxial arrangement enhance the structural stability and reliability of the jet pump, enabling it to better adapt to different operating conditions and extend its service life. Furthermore, the optimized fluid flow path and component parameters improve fluid mixing and energy conversion efficiency, reduce flow losses, and thus comprehensively enhance the performance and efficiency of the jet pump. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the external structure of a dual-nozzle jet pump according to an embodiment of the present invention;

[0018] Figure 2 This is a schematic diagram of the internal structure of a dual-nozzle jet pump according to an embodiment of the present invention;

[0019] Figure 3 This is a schematic diagram of the nozzle assembly.

[0020] Figure 4 for Figure 1 An enlarged view of the inlet cavity shown;

[0021] Figure 5 The diagram shows the internal pressure distribution of a conventional single-nozzle jet pump and a dual-nozzle jet pump according to an embodiment of the present invention during operation. Detailed Implementation

[0022] To better understand the purpose, structure, and function of this invention, the invention will be described in further detail below with reference to the accompanying drawings.

[0023] Figure 1 and Figure 2 The structure of a dual-nozzle jet pump 100 according to an embodiment of the present invention is shown. Figure 1 and Figure 2 As shown, the dual-nozzle jet pump 100 may include: a pump body 101, in which a working fluid channel 1 and a conveyed fluid channel 10 are formed, the working fluid inlet of the working fluid channel is located at the top of the jet pump 100, and the conveyed fluid inlet of the conveyed fluid channel 10 is located at the bottom of the jet pump 100; a sleeve 3 sleeved outside the pump body 101, and a mixed fluid discharge channel 2 is formed between the pump body and the sleeve 3; a pump core 102 disposed inside the pump body 101, the pump core 102 may include an inlet cavity 4 connected to the working fluid channel 1, nozzles 6 symmetrically connected to both ends of the inlet cavity 4 along the axial direction, throats 7 arranged at intervals with the outlets of each nozzle 6, and diffusers 8 connected to the outlets of each throat 7, the diffusers 8 being connected to the mixed fluid discharge channel 2, and the conveyed fluid channel 10 being connected to the nozzles 6. The working fluid enters the inlet cavity 4 through the working fluid channel 1 and simultaneously enters the nozzles 6 at both ends. A low-pressure zone is formed at the outlet of the nozzle 6, which causes the fluid to be transported to be drawn into the nozzle 6 through the transported fluid channel 10. After merging with the working fluid therein, the fluid enters the throat 7 and is fully mixed to form a high-speed mixed fluid. The high-speed mixed fluid is pressurized through the diffuser 8 and discharged through the mixed fluid discharge channel 2.

[0024] In this embodiment of the invention, the dual-nozzle jet pump 100 operates by introducing working fluid from the working fluid inlet at the top of the pump 100 through the working fluid channel 1 into the inlet cavity 4 within the pump body 101. After being uniformly distributed within the inlet cavity 4, the working fluid flows into nozzles 6, which are symmetrically connected at both ends of the inlet cavity 4 along the axial direction. As the working fluid passes through the nozzles 6, due to the tapered shape of the nozzles 6, the cross-sectional area gradually decreases. According to Bernoulli's principle, the fluid velocity increases significantly, while the pressure decreases accordingly, forming a low-pressure zone at the nozzle 6 outlet. The conveyed fluid channel 10 at the bottom of the jet pump 100 is connected to the nozzles 6, and the low-pressure zone at the nozzle 6 outlet is connected to the conveyed fluid channel 10. A pressure difference is generated between the ambient pressure at the inlet of the conveying fluid and the pressure at the nozzle 6. This pressure difference causes the conveyed fluid to be drawn into the nozzle 6 through the conveyed fluid channel 10, where it merges with the high-speed working fluid. After merging at the outlet of the nozzle 6, the working fluid and the conveyed fluid enter the throat 7 through the suction chamber 11. The high-speed kinetic energy of the working fluid is transferred to the conveyed fluid, causing its velocity to increase rapidly, forming a high-speed mixed fluid. The high-speed mixed fluid enters the diffuser 8 from the throat 7. As the mixed fluid flows within the diffuser, its cross-sectional area gradually increases, and its velocity decreases. According to Bernoulli's principle, the pressure increases accordingly, realizing the conversion of kinetic energy into pressure energy. Finally, the mixed fluid exits the jet pump 100 through the mixed fluid discharge channel 2 between the sleeve 3 and the pump body 101 via the diffuser outlet 9, completing the fluid conveying process. The entire working process is continuous, achieving efficient and stable fluid conveying through the synergistic action of various components.

[0025] The dual-nozzle jet pump 100 of this embodiment adopts a dual-nozzle structure, allowing the working fluid to simultaneously enter both nozzles 6. This not only creates a symmetrically expanded low-pressure zone at the nozzle 6 outlet but also achieves dynamic flow field balance. Compared to the traditional single-nozzle structure, it can significantly increase the flow rate of the transported fluid under the same working fluid flow rate, thereby improving the jet pump's delivery efficiency. By placing the working fluid inlet at the top and the transported fluid inlet at the bottom, the working fluid flows from top to bottom, while the transported fluid flows from bottom to top. This allows the working fluid to more smoothly draw in the transported fluid using gravity and pressure difference, further increasing the flow rate of the transported fluid and improving the jet pump's delivery efficiency. Furthermore, by separating the working fluid channel 1, the transported fluid channel 10, and the mixed fluid discharge channel 2 and arranging them rationally with the pump core 102, the dual-nozzle jet pump 100 of this embodiment not only effectively avoids flow field interference and reduces energy loss but also makes the overall structure of the dual-nozzle jet pump 100 of this embodiment more compact and easier to connect to external pipelines.

[0026] In such Figure 2 and Figure 4In the preferred embodiment shown, the inlet cavity 4 may include a constant diameter section 41 and tapered sections 42 symmetrically connected to both ends of the constant diameter section 41. The tapered sections 42 have an inner diameter that tapers from the constant diameter section 41 toward the nozzle 6. In this embodiment, the design of the constant diameter section 41 and the tapered sections 42 at both ends of the inlet cavity 4 allows the working fluid to gradually accelerate as it flows from the constant diameter section 41 to the nozzle 6, reducing fluid separation and eddy current generation. The working fluid can be evenly distributed before entering the two nozzles 6, ensuring that a stable low-pressure zone is formed at the outlet of both nozzles 6, thereby more effectively drawing in the transported fluid and improving the uniformity and stability of the transported fluid flow rate.

[0027] Preferably, the contact surfaces of the two conical sections 42 and the equal diameter section 41, as well as the connection between the two conical sections 42 and the nozzle 6, are all subjected to sealing reinforcement treatment, and high temperature resistant sealing alloy material is preferably selected, which can effectively prevent fluid leakage under high pressure differential and improve the reliability and service life of the jet pump 100 under harsh working conditions such as high temperature and high pressure.

[0028] In such Figure 2 In the preferred embodiment shown, inlet cavity channels 5 are symmetrically arranged on opposite sides of the inlet cavity 4, and the inlet cavity channels 5 are connected to the working fluid channel 1. This arrangement allows the working fluid to be evenly distributed to the inlet cavity 5, ensuring that the working fluid enters the inlet cavity 4 stably and uniformly, eliminating the flow deviation caused by unilateral fluid inlet, and also avoiding the impact of pressure fluctuations or uneven flow at the working fluid inlet on the normal operation of the jet pump 100, thereby helping to improve the working stability and performance of the pump core 102.

[0029] Preferably, the inlet inner cavity channel 5 is made of a high-pressure resistant material, and the inlet inner cavity channel 5 and the inlet inner cavity 4 should be tightly connected to prevent high-pressure fluid leakage, thereby improving system safety.

[0030] According to a preferred embodiment of the present invention, the outlet diameter d of the nozzle 6 is ≤3.5mm, and the inlet diameter is 1.25d to 1.3d. In this embodiment, with an outlet diameter d ≤3.5mm, the outlet flow velocity of the nozzle 6 is significantly increased under the same working pressure, expanding the intensity of the low-pressure zone. Optimizing the inlet diameter to 1.25d to 1.3d avoids flow restriction due to an excessively small inlet diameter or insufficient acceleration due to an excessively large inlet diameter, thus achieving a balance between flow velocity and flow rate. By limiting the ratio range of the outlet diameter and inlet diameter of the nozzle 6, this embodiment can precisely control the flow channel shape and size of the nozzle 6, enabling the working fluid to achieve a higher velocity when passing through the nozzle 6, while forming a more significant low-pressure zone at the outlet of the nozzle 6, enhancing the suction capacity of the conveyed fluid, promoting thorough mixing of the working fluid and the conveyed fluid, improving the mixing effect and the performance of the jet pump.

[0031] Furthermore, in a preferred embodiment, the distance between the outlet of the nozzle 6 and the inlet of the throat 7 can be 1.2d to 1.35d. Since an excessively large distance between the outlet of the nozzle 6 and the throat 7 would weaken the low-pressure zone, while an excessively small distance would hinder the entry of the fluid being drawn in, this embodiment, by controlling the distance between the outlet of the nozzle 6 and the inlet of the throat 7 within a specific range, facilitates the formation of a good fluid flow state at the inlet of the throat 7. This allows the working fluid and the fluid being transported to mix fully at this point, avoiding problems such as insufficient mixing due to an excessively small distance or flow separation due to an excessively large distance. This ensures the quality of the mixed fluid and the efficiency of subsequent energy conversion.

[0032] According to a preferred embodiment of the present invention, the ratio of the inner cavity area of ​​the throat 7 to the inner cavity area of ​​the nozzle 6 can be 3.5 to 4. This arrangement allows the mixed fluid to have a suitable flow velocity and flow state within the throat 7, which is beneficial for the kinetic energy of the working fluid to be fully transferred to the fluid being transported, thereby improving the mixing efficiency. It also helps to reduce flow losses within the throat 7 and improve the overall performance of the jet pump 100.

[0033] Furthermore, the length of the throat 7 can be 6 to 8 times the inner diameter of the throat. This arrangement provides sufficient mixing length for the working fluid and the fluid being transported, ensuring that the two fluids are fully mixed within the throat 7 to form a uniform, high-speed mixed fluid. This, in turn, improves the energy level and quality of the mixed fluid, creating favorable conditions for subsequent energy conversion within the diffuser 8.

[0034] In another preferred embodiment, the diffuser 8 can be a single-angle diffuser with a diffusion angle of 5–8°. This design allows the mixed fluid to smoothly convert kinetic energy into pressure energy within the diffuser 8, reducing flow losses, increasing the head and efficiency of the jet pump, and also helping to ensure the structural strength and rigidity of the diffuser.

[0035] Furthermore, the length of the diffuser 8 is not less than four times the inner diameter of the throat 7. This arrangement ensures that the mixed fluid has sufficient time and space to complete the energy conversion process within the diffuser 8, thereby significantly increasing the pressure of the mixed fluid and thus improving the outlet pressure and delivery capacity of the jet pump 100.

[0036] According to the present invention, in such Figure 3 In the preferred embodiment shown, the inlet cavity 4, nozzle 6, throat 7, and diffuser 8 can be arranged coaxially. This embodiment ensures smoother fluid flow between components, reduces energy loss during flow, improves the working efficiency and performance stability of the jet pump, and also helps to improve the structural compactness of the jet pump 100.

[0037] Figure 1 below shows a comparison of the structural parameters between a conventional single-nozzle jet pump and the dual-nozzle jet pump 100 of this embodiment of the invention. As can be seen from Figure 1, under the same working fluid flow rate, diffuser angle, throat-to-nozzle distance, throat-to-nozzle area ratio, average working fluid flow rate, minimum working fluid flow rate, and maximum working fluid flow rate, the liquid flow rate drawn by the dual-nozzle jet pump 100 of this embodiment of the invention is greater than that drawn by the conventional single-nozzle jet pump. This demonstrates that the dual-nozzle jet pump 100 of this embodiment of the invention has superior suction performance.

[0038] Table 1

[0039] Throat inner diameter combination (mm) 4.49-8.4 3.21-6.01 Single nozzle diameter (mm) 4.49 3.21 Single throat diameter (mm) 8.4 6.01 throat to nozzle area ratio 3.504 3.505 Throat-mouth distance (m) 1.25d 1.25d Length of the trachea (mm) 58.8 42.07 Diffuser tube length (mm) 132.842 160.212 diffuser angle 5° 5° Working fluid pressure (MPa) 26.5 26.5 <![CDATA[Average working fluid flow rate (m 3 / h)]]> 242.9 242.9 <![CDATA[Average liquid suction flow rate (m 3 / h)]]> 219.31 248.6 Ratio of average drawn-out fluid flow rate to average working fluid flow rate 0.903 1.025 <![CDATA[Maximum working fluid flow rate (m 3 / h)]]> 243.09 243.09 <![CDATA[Maximum liquid suction flow rate (m 3 / h)]]> 224.46 252.42 Ratio of maximum absorbed liquid flow rate to maximum working liquid flow rate 0.923 1.04 <![CDATA[Minimum working fluid flow rate ( m 3 / h)]]> 242.73 242.73 <![CDATA[Minimum liquid suction flow rate (m 3 / h)]]> 213.85 242.25 Ratio of minimum absorbed liquid flow rate to minimum working liquid flow rate 0.881 0.999

[0040] Figure 5 The diagram illustrates the internal pressure distribution of a conventional single-nozzle jet pump (top) and a dual-nozzle jet pump 100 (bottom) according to an embodiment of the present invention during operation. Figure 5 As shown, the pressure value at the nozzle of the existing single-nozzle jet pump is 7.5538, while the pressure values ​​at the two nozzles of the dual-nozzle jet pump of this embodiment are 6.91639 and 7.17309, respectively. It can be seen that the pressure values ​​at the two nozzles of the dual-nozzle jet pump of this embodiment are both lower than the pressure values ​​at the nozzle of the existing single-nozzle jet pump. This further verifies that the suction force generated at the two nozzles of the dual-nozzle jet pump of this embodiment is superior to that of the nozzle of the existing single-nozzle jet pump.

[0041] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. These modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention, and they should all be covered within the scope of the claims and specification of the present invention. In particular, as long as there is no structural conflict, the various technical features mentioned in the embodiments can be combined in any way. The present invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A dual-nozzle jet pump, characterized in that, include: The pump body has a working fluid channel and a conveyed fluid channel formed therein. A sleeve is fitted over the outside of the pump body, and a mixed fluid discharge channel is formed between the pump body and the sleeve; The pump core disposed within the pump body includes an inlet cavity communicating with the working fluid channel, nozzles symmetrically connected to both ends of the inlet cavity along the axial direction, throats spaced apart from the outlets of each nozzle, and diffuser tubes communicating with the outlets of each throat tube. The diffuser tubes are connected to the mixed fluid discharge channel, and the conveyed fluid channel is connected to the nozzles. The working fluid enters the inlet cavity through the working fluid channel and simultaneously enters the nozzles at both ends. A low-pressure zone is formed at the outlet of the nozzle, causing the fluid to be transported to be drawn into the nozzle through the transported fluid channel. After merging with the working fluid therein, the fluid enters the throat and is fully mixed to form a high-speed mixed fluid. The high-speed mixed fluid is pressurized through the diffuser and then discharged through the mixed fluid discharge channel. The inlet cavity includes a constant diameter section and tapered sections symmetrically connected to both ends of the constant diameter section, the tapered sections having an inner diameter that tapers in the direction from the constant diameter section toward the nozzle; The inlet cavity is symmetrically provided with inlet cavity channels on both sides opposite to each other, and the inlet cavity channels are connected to the working fluid channel; The nozzle has an outlet diameter d ≤ 3.5 mm and an inlet diameter of 1.25 d ~ 1.3 d; The distance between the outlet of the nozzle and the inlet of the throat is 1.2d to 1.35d; The ratio of the inner area of ​​the throat to the inner area of ​​the nozzle is 3.5 to 4. The length of the larynx is 6 to 8 times the inner diameter of the larynx.

2. The dual-nozzle jet pump according to claim 1, characterized in that, The diffuser tube is a single-angle diffuser tube with a diffusion angle of 5~8°.

3. The dual-nozzle jet pump according to claim 2, characterized in that, The length of the diffuser tube is not less than four times the inner diameter of the throat tube.

4. The dual-nozzle jet pump according to claim 1, characterized in that, The inlet cavity, the nozzle, the throat, and the diffuser are arranged coaxially.

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