Double-nozzle jet pump

Abstract

The invention belongs to the technical field of jet pump equipment, and discloses a double-nozzle jet pump capable of improving suction efficiency. A working fluid channel, a conveyed fluid channel and a pump core are formed in the pump body; the pump body is sleeved with the sleeve, and a mixed fluid discharging channel is formed between the sleeve and the sleeve; the pump core comprises an inlet inner cavity connected with the working fluid channel, nozzles symmetrically connected to the two ends of the inlet inner cavity in the axial direction, a throat pipe arranged at intervals with outlets of the nozzles and a diffusion pipe connected with an outlet of the throat pipe, the diffusion pipe is communicated with the mixed fluid discharging channel, and the conveyed fluid channel is communicated with the nozzles. Working fluid enters the inlet inner cavity through the working fluid channel and then enters the nozzles at the two ends of the inlet inner cavity at the same time, low-pressure areas are formed at outlets of the nozzles so that conveyed fluid can be sucked into the nozzles through the conveyed fluid channel, and the conveyed fluid and the working fluid in the conveyed fluid channel are converged and then enter the throat pipe to be mixed to form high-speed mixed fluid. And the high-speed mixed fluid is discharged through the mixed fluid discharge channel after being pressurized by the diffusion pipe.

Description

Technical Field

[0001] The present invention relates to the technical field of jet pump equipment, in particular to a double-nozzle jet pump. Background Art

[0002] Jet pumps, as devices with no moving parts that use high-speed fluid entrainment to transport media, are widely used in oil extraction, chemical processes, mine drainage, and other fields due to their simple structure and low maintenance costs. Their core principle follows the Bernoulli equation: the working fluid is accelerated through the nozzle, creating a low-pressure zone, which entrains the conveyed fluid. The two fluids mix in the throat and then pass through the diffuser, converting kinetic energy into pressure energy for output.

[0003] However, existing jet pumps usually use a single nozzle, which has two inherent defects: 1) The low-pressure area generated by the single nozzle structure is limited, and the suction capacity of the conveyed fluid is insufficient, resulting in low suction efficiency. Experimental data show (see Table 1) that the suction flow rate of the traditional pump at a working pressure of 26.5 MPa is only 219.31 m 3 / h, and the flow ratio (suctioned fluid flow / working fluid flow) is as low as 0.903, greatly limiting the jet pump's suction efficiency. 2) Severe flow channel energy loss: When the working fluid enters the inlet cavity, turbulent impact is easily generated, resulting in kinetic energy loss. In particular, attempts to increase the flow rate by increasing the number of nozzles will cause flow interference, further exacerbating energy loss.

[0004] Although existing technologies attempt to optimize nozzle parameters (such as throat-to-nozzle distance, diffusion angle, etc.), existing jet pumps have not been able to break through the bottleneck of suction efficiency. Summary of the Invention

[0005] In order to improve the suction efficiency, the present invention proposes a double-nozzle jet pump.

[0006] The double-nozzle jet pump according to the present invention comprises: a pump body, in which a working fluid channel and a conveyed fluid channel are formed; a sleeve sleeved on the outside of the pump body, a mixed fluid discharge channel is formed between the pump body and the sleeve; a pump core arranged in the pump body, the pump core comprising an inlet cavity connected to 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 connected to the outlets of each throat, the diffusers being connected to the mixed fluid discharge channel, and the conveyed fluid channel being connected to the nozzles. The working fluid enters the inlet cavity through the working fluid channel and simultaneously enters the nozzles at both ends thereof, forming a low-pressure area at the outlet of the nozzle so that the conveyed fluid is sucked into the nozzle through the conveyed fluid channel, and after merging with the working fluid therein, enters the throat pipe and is fully mixed 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 inner cavity includes a constant diameter section and tapered sections symmetrically connected to both ends of the constant diameter section, and the tapered section has an inner diameter that gradually contracts in a direction from the constant diameter section toward the nozzle.

[0008] Furthermore, inlet inner cavity channels are symmetrically provided on two opposite sides of the inlet inner cavity, and the inlet inner cavity channels are communicated with the working fluid channel.

[0009] Furthermore, the nozzle has an outlet diameter d≤3.5 mm and an inlet diameter of 1.25 d to 1.3 d.

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

[0011] Furthermore, the ratio of the inner cavity area of the throat tube to the inner cavity area of the nozzle is 3.5-4.

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

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

[0014] Furthermore, the length of the diffuser is not less than 4 times the inner diameter of the throat pipe.

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

[0016] Compared with the prior art, the dual-nozzle jet pump of the present invention adopts a unique dual-nozzle structure and optimizes the size, shape, spacing, and layout of components such as the inlet inner cavity, nozzle, throat, and diffuser. This can effectively increase the flow rate of the conveyed fluid while maintaining the same working fluid flow rate, thereby significantly improving the delivery efficiency of the jet pump. At the same time, the sealing reinforcement 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 working conditions and extend its service life. In addition, the optimized fluid flow path and the parameters of each component are conducive to improving the mixing effect and energy conversion efficiency of the fluid, reducing flow losses, and thus improving the overall performance and working efficiency of the jet pump. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 Schematic diagram of the external structure of a double-nozzle jet pump according to an embodiment of the present invention;

[0018] Figure 2 Schematic diagram of the internal structure of a double-nozzle jet pump according to an embodiment of the present invention;

[0019] Figure 3 Schematic diagram of the structure of the nozzle assembly;

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

[0021] Figure 5 The diagram shows the internal pressure distribution of the existing single-nozzle jet pump and the double-nozzle jet pump according to the embodiment of the present invention during operation. DETAILED DESCRIPTION

[0022] In order to better understand the purpose, structure and function of the present invention, the present invention is further described in detail below with reference to the accompanying drawings.

[0023] Figure 1 and Figure 2 FIG. 2 shows the structure of a double-nozzle jet pump 100 according to an embodiment of the present invention. Figure 1 and Figure 2 As shown, the double-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 arranged at the top of the jet pump 100, and the conveyed fluid inlet of the conveyed fluid channel 10 is arranged at the bottom of the jet pump 100; a sleeve 3 is sleeved on the outside of 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 is arranged in the pump body 101, and 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 from the outlets of each nozzle 6, and diffusers 8 connected to the outlets of each throat 7, the diffuser 8 is connected to the mixed fluid discharge channel 2, and the conveyed fluid channel 10 is connected to the nozzle 6. Among them, the working fluid enters the inlet cavity 4 through the working fluid channel 1 and enters the nozzles 6 at both ends at the same time, forming a low-pressure area at the outlet of the nozzle 6, so that the conveyed fluid is sucked into the nozzle 6 through the conveyed fluid channel 10, and after merging with the working fluid therein, they enter the throat 7 together and are fully mixed to form a high-speed mixed fluid. The high-speed mixed fluid is pressurized by the diffuser 8 and then discharged through the mixed fluid discharge channel 2.

[0024] When the dual-nozzle jet pump 100 of the embodiment of the present invention is working, the working fluid enters the inlet cavity 4 in the pump body 101 through the working fluid channel 1 from the working fluid inlet at the top of the jet pump 100. After the working fluid is evenly divided in the inlet cavity 4, it flows into the nozzles 6 connected to the two ends of the inlet cavity 4 in an axially symmetrical manner. When the working fluid passes through the nozzle 6, due to the tapered shape of the nozzle 6, the cross-sectional area gradually decreases. According to the Bernoulli principle, the fluid velocity increases significantly, while the pressure decreases accordingly, forming a low-pressure area at the outlet of the nozzle 6. The conveyed fluid channel 10 at the bottom of the jet pump 100 is connected to the nozzle 6. The low-pressure area at the outlet of the nozzle 6 is connected to the conveyed fluid. A pressure differential is created between the ambient pressure at the inlet of the transported fluid and the ambient pressure, causing the transported fluid to be drawn into the nozzle 6 through the transported fluid channel 10, where it merges with the high-speed working fluid therein. After the working fluid and the transported fluid merge at the outlet of the nozzle 6, they pass through the suctioned liquid chamber 11 and enter the throat 7 together. The high-speed kinetic energy of the working fluid is transferred to the transported fluid, rapidly increasing its velocity and forming a high-speed mixed fluid. From the throat 7, the high-speed mixed fluid enters the diffuser 8. 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, converting kinetic energy into pressure energy. Finally, the mixed fluid enters the mixed fluid discharge channel 2 between the sleeve 3 and the pump body 101 through the diffuser outlet 9 and exits the jet pump 100, completing the fluid transport process. The entire process proceeds continuously, and through the synergistic effect of various components, efficient and stable fluid transport is achieved.

[0025] The double-nozzle jet pump 100 of the embodiment of the present invention adopts a double-nozzle structure, and the working fluid enters the nozzles 6 at both ends at the same time, which not only forms a symmetrically expanded low-pressure area at the outlet of the nozzle 6, but also realizes the dynamic balance of the flow field. Compared with the traditional single-nozzle structure, under the same working fluid flow rate, the flow rate of the conveyed fluid can be significantly increased, thereby improving the delivery efficiency of the jet pump; by arranging the working fluid inlet at the top and the conveyed fluid inlet at the bottom, the working fluid flows from top to bottom and the conveyed fluid flows from bottom to top, so that the working fluid can utilize gravity and pressure difference to more smoothly absorb the conveyed fluid, which helps to further increase the flow rate of the conveyed fluid and improve the delivery efficiency of the jet pump; in addition, the double-nozzle jet pump 100 of the embodiment of the present invention separates the working fluid channel 1, the conveyed fluid channel 10 and the mixed fluid discharge channel 2 and arranges them reasonably with the pump core 102, which not only effectively avoids flow field interference and reduces energy loss, but also makes the overall structure of the double-nozzle jet pump 100 of the embodiment of the present invention more compact and convenient for connection to external pipelines.

[0026] In such Figure 2 and Figure 4In the preferred embodiment shown, the inlet lumen 4 may include a constant diameter section 41 and tapered sections 42 symmetrically connected at 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 lumen 4 gradually accelerates the working fluid as it flows from the constant diameter section 41 toward the nozzle 6, reducing fluid separation and vortex generation. The working fluid is 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 inhaling the conveyed fluid and improving the uniformity and stability of the conveyed fluid flow rate.

[0027] Preferably, the contact surfaces between the two conical sections 42 and the equal-diameter section 41 and 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 materials are preferably selected to effectively prevent fluid leakage under the action of high pressure difference, thereby improving 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 disposed on opposite sides of the inlet cavity 4, communicating with the working fluid channel 1. This arrangement allows the working fluid to be evenly distributed to the inlet cavity 5, ensuring stable and uniform entry of the working fluid into the inlet cavity 4, eliminating biased flow caused by unilateral inflow. It also prevents pressure fluctuations or uneven flow at the working fluid inlet from affecting the normal operation of the jet pump 100, thereby improving the operating stability and performance of the pump core 102.

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

[0030] According to the present invention, in a preferred embodiment, the outlet diameter d of the nozzle 6 is ≤3.5mm, and the inlet diameter is 1.25d~1.3d. In this embodiment, the outlet diameter d of the nozzle 6 is ≤3.5mm. Under the same working pressure, the outlet flow rate of the nozzle 6 is significantly improved, and the strength of the low-pressure zone is expanded. Optimizing the inlet diameter so that the inlet diameter is 1.25d~1.3d can avoid the flow restriction caused by too small an inlet diameter, or insufficient acceleration caused by too large an inlet diameter, thereby achieving the purpose of balancing the flow rate and flow rate. By limiting the ratio range of the outlet diameter and the inlet diameter of the nozzle 6, this embodiment can accurately control the flow channel shape and size of the nozzle 6, so that the working fluid can obtain a higher speed when passing through the nozzle 6, and at the same time, form a more significant low-pressure zone at the outlet of the nozzle 6, thereby enhancing the suction capacity of the conveyed fluid, promoting the full mixing of the working fluid and the conveyed fluid, and 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 a larger distance between the outlet of the nozzle 6 and the throat 7 weakens the strength of the low-pressure zone, while a smaller distance hinders the entry of the sucked fluid, this embodiment controls the distance between the outlet of the nozzle 6 and the inlet of the throat 7 within a specific range, which facilitates the formation of a good fluid flow state at the inlet of the throat 7, allowing the working fluid and the conveyed fluid to be fully mixed there, avoiding problems such as insufficient mixing due to a too small distance or flow separation due to an excessive distance, thereby ensuring the quality of the mixed fluid and the efficiency of subsequent energy conversion.

[0032] According to the present invention, in a preferred embodiment, the ratio of the inner cavity area of the throat pipe 7 to the inner cavity area of the nozzle 6 can be 3.5 to 4. This setting can ensure that the mixed fluid has a suitable flow rate and flow state in the throat pipe 7, which is conducive to fully transferring the kinetic energy of the working fluid to the conveyed fluid, improving the mixing efficiency, and also helps to reduce flow losses in the throat pipe 7, thereby improving the overall performance of the jet pump 100.

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

[0034] In another preferred embodiment, the diffuser 8 can be a single-angle diffuser with a diffusion angle of 5 to 8 degrees. This design allows the mixed fluid to smoothly convert kinetic energy into pressure energy within the diffuser 8, reducing flow losses, improving 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 4 times the inner diameter of the throat 7. This arrangement ensures that the mixed fluid has enough time and space in the diffuser 8 to complete the energy conversion process, so that the pressure of the mixed fluid is fully increased, thereby improving the outlet pressure and delivery capacity of the jet pump 100.

[0036] According to the present invention, Figure 3 In the preferred embodiment shown, the inlet cavity 4, nozzle 6, throat 7, and diffuser 8 can be coaxially arranged. This embodiment is used to ensure smoother fluid flow between the various components, reduce energy loss during the flow process, improve the efficiency and performance stability of the jet pump, and also help improve the structural compactness of the jet pump 100.

[0037] Table 1 below compares the structural parameters of an existing single-nozzle jet pump and a dual-nozzle jet pump 100 according to an embodiment of the present invention. As shown in Table 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 dual-nozzle jet pump 100 according to the embodiment of the present invention achieves a higher suction flow rate than the existing single-nozzle jet pump, demonstrating that the dual-nozzle jet pump 100 according to the embodiment of the present invention exhibits superior suction performance.

[0038] Table 1

[0039] Pump Type Comparison Single nozzle New pump Nozzle 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-to-mouth distance (m) 1.25d 1.25d Throat length (mm) 58.8 42.07 Diffuser 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 absorption flow rate (m 3 / h)]]> 219.31 248.6 Ratio of average sucked liquid flow to average working liquid flow 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 sucked liquid flow to maximum working liquid flow 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 sucked liquid flow to minimum working liquid flow 0.881 0.999

[0040] Figure 5 The diagram shows the pressure distribution inside the existing single nozzle jet pump (upper diagram) and the double nozzle jet pump 100 (lower diagram) of the 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 displayed as 7.5538, and the pressure values at the two nozzles of the dual-nozzle jet pump in the embodiment of the present invention are displayed as 6.91639 and 7.17309 respectively. It can be seen that the pressure values at the two nozzles of the dual-nozzle jet pump in the embodiment of the present invention are smaller than the pressure value at the nozzle of the existing single-nozzle jet pump, which further verifies that the suction force generated at the two nozzles of the dual-nozzle jet pump in the embodiment of the present invention is better than 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, rather than to limit them. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some or all of the technical features therein. These modifications or replacements do not deviate the essence of the corresponding technical solutions from the scope of the technical solutions of the embodiments of the present invention, and they should all be included in the scope of the claims and description of the present invention. In particular, as long as there is no structural conflict, the various technical features mentioned in the various embodiments can be combined in any way. The present invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions that fall within the scope of the claims.

Claims

1. A double nozzle jet pump, characterized in that, include: A pump body, wherein a working fluid channel and a conveyed fluid channel are formed in the pump body; A sleeve is sleeved on the outside of the pump body, and a mixed fluid discharge channel is formed between the pump body and the sleeve; A pump core is provided in the pump body, the pump core comprising an inlet inner cavity connected to the working fluid channel, nozzles symmetrically connected to both ends of the inlet inner cavity along the axial direction, throat pipes spaced apart from the outlets of the nozzles, and diffusers connected to the outlets of the throat pipes, the diffusers being connected to the mixed fluid discharge channel, and the transported fluid channel being connected to the nozzles. Among them, the working fluid enters the inlet cavity through the working fluid channel and enters the nozzles at both ends at the same time, forming a low-pressure area at the outlet of the nozzle, so that the conveyed fluid is sucked into the nozzle through the conveyed fluid channel, and after merging with the working fluid therein, they enter the throat together and are fully mixed to form a high-speed mixed fluid. The high-speed mixed fluid is pressurized by the diffuser and then discharged through the mixed fluid discharge channel.

2. The double-nozzle jet pump according to claim 1, characterized in that: The inlet inner cavity includes a constant diameter section and tapered sections symmetrically connected to both ends of the constant diameter section, and the tapered section has an inner diameter that gradually contracts in a direction from the constant diameter section toward the nozzle.

3. The double-nozzle jet pump according to claim 1 or 2, characterized in that: Inlet inner cavity channels are symmetrically provided on two opposite sides of the inlet inner cavity, and the inlet inner cavity channels are communicated with the working fluid channel.

4. The double-nozzle jet pump according to claim 1 or 2, characterized in that: The outlet diameter d of the nozzle is ≤3.5 mm, and the inlet diameter is 1.25 d to 1.3 d.

5. The double-nozzle jet pump according to claim 4, characterized in that: The distance between the outlet of the nozzle and the inlet of the throat pipe is 1.2d to 1.35d.

6. The double-nozzle jet pump according to claim 5, characterized in that: The ratio of the inner cavity area of the throat tube to the inner cavity area of the nozzle is 3.5-4.

7. The double-nozzle jet pump according to claim 6, characterized in that: The length of the throat pipe is 6 to 8 times the inner diameter of the throat pipe.

8. The double-nozzle jet pump according to claim 4, characterized in that: The diffusion tube is a single-angle diffusion tube with a diffusion angle of 5 to 8 degrees.

9. The double-nozzle jet pump according to claim 8, characterized in that: The length of the diffusion pipe is not less than 4 times the inner diameter of the throat pipe.

10. The double-nozzle jet pump according to claim 1 or 2, characterized in that: The inlet cavity, the nozzle, the throat pipe and the diffuser are coaxially arranged.

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