CN114665686B

CN114665686B - Spiral electromagnetic pump

Info

Publication number: CN114665686B
Application number: CN202210375904.7A
Authority: CN
Inventors: 王冲; 徐帅; 杨红义; 余华金; 陈树明; 周立军; 吕明宇; 邰永; 杨晓茜; 梁胜莹
Original assignee: China Institute of Atomic of Energy
Current assignee: China Institute of Atomic of Energy
Priority date: 2022-04-11
Filing date: 2022-04-11
Publication date: 2023-08-18
Anticipated expiration: 2042-04-11
Also published as: CN114665686A

Abstract

The spiral electromagnetic pump comprises a pump groove outer shell, a pump groove inner shell, a pump groove pipeline, a first spiral blade, a second spiral blade and an electromagnetic driving device. The pump channel housing defines a receiving chamber, and a radial peripheral wall of the pump channel housing is provided with a fluid inlet communicating with the receiving chamber. The pump ditch inner shell is arranged in the accommodating cavity. One part of the pump ditch pipeline is positioned in the accommodating cavity, and the other part extends from one side axial end wall of the pump ditch shell to the outside of the accommodating cavity. An outer annular flow passage is formed between the pump ditch pipeline and the pump ditch outer shell, and an inner annular flow passage communicated with the outer annular flow passage is formed between the pump ditch pipeline and the pump ditch inner shell. The first spiral vane is arranged between the pump ditch pipeline and the pump ditch shell so as to form an outer layer spiral flow passage in the outer layer annular flow passage; the second helical blade is arranged between the pump ditch pipeline and the pump ditch inner shell so as to form an inner layer helical flow passage in the inner layer annular flow passage. The electromagnetic driving device is used for providing electromagnetic force for driving the liquid metal to flow from the liquid inlet to the inner spiral flow passage along the outer spiral flow passage.

Description

Spiral electromagnetic pump

Technical Field

The application relates to the technical field of electromagnetic pumps, in particular to a spiral electromagnetic pump.

Background

The electromagnetic pump is used as important liquid metal conveying equipment, and has the advantages of no medium contact, no moving parts, complete sealing, simple maintenance and the like, so that the electromagnetic pump is widely applied to the nuclear power field.

In the common application scenario of electromagnetic pumps, the size factor of the electromagnetic pump is not considered, and therefore, the electromagnetic pump has a larger size. However, in some special application scenarios, such as some vehicle-mounted devices or underwater devices, the total space of the system is limited, and the electromagnetic pump is required to be small in size and have a high lift.

Disclosure of Invention

The application aims to provide a spiral electromagnetic pump with small volume and high lift.

In order to achieve the above object, an embodiment of the present application provides a screw electromagnetic pump including:

a pump trough housing defining a receiving cavity, a radial peripheral wall of the pump trough housing being provided with a liquid flow inlet communicating with the receiving cavity for receiving liquid metal;

the pump groove inner shell is arranged in the accommodating cavity;

the two axial ends of the pump ditch pipeline are open ends, one part of the pump ditch pipeline is positioned in the accommodating cavity, the other part of the pump ditch pipeline extends from one axial end wall of one side of the pump ditch shell to the outside of the accommodating cavity, an outer annular flow channel is formed between the pump ditch pipeline and the pump ditch shell, an inner annular flow channel communicated with the outer annular flow channel is formed between the pump ditch pipeline and the pump ditch inner shell, and therefore liquid metal entering the accommodating cavity through the liquid flow inlet sequentially flows through the outer annular flow channel and the inner annular flow channel and flows out from the open end of the pump ditch pipeline positioned outside the accommodating cavity;

the first spiral vane is arranged between the pump ditch pipeline and the pump ditch shell so as to form an outer layer spiral flow passage in the outer layer annular flow passage;

the second helical blade is arranged between the pump ditch pipeline and the pump ditch inner shell so as to form an inner layer helical flow passage in the inner layer annular flow passage; and

and the electromagnetic driving device is used for providing electromagnetic force for driving the liquid metal to flow from the liquid inlet to the inner spiral flow passage along the outer spiral flow passage.

Drawings

Other objects and advantages of the present application will become apparent from the following description of the application with reference to the accompanying drawings, which provide a thorough understanding of the present application.

FIG. 1 is a schematic cross-sectional view of a screw electromagnetic pump according to one embodiment of the application;

FIG. 2 is an enlarged view of a portion of the solenoid pump of FIG. 1;

FIG. 3 is a schematic view of the pump channel tubing shown in FIG. 1; and

fig. 4 is a schematic view of the construction of the pump groove inner housing shown in fig. 1.

It should be noted that the drawings are not necessarily to scale, but are merely shown in a schematic manner that does not affect the reader's understanding.

Reference numerals illustrate:

100. a screw electromagnetic pump;

10. a pump groove inner shell; 102. an inner annular flow passage; 11. a straight pipe section; 111. a second helical blade; 112. a second flow guiding part; 12. a diversion section;

20. a pump groove housing; 201. a liquid flow inlet; 202. an outer annular flow passage; 21. a receiving chamber; 22. a radial peripheral wall; 23. an axial end wall;

30. a pump ditch pipe; 301. an open end; 31. a first helical blade; 32. a first flow guiding part; 321. a first sidewall; 322. a second sidewall; 323. connecting the side walls; 33. an axial end face;

40. an inner core; 50. an outer core; 60. a coil; 70. and a heat insulation layer.

Detailed Description

In order to make the objects, technical solutions and advantages of the present application more apparent, the technical solutions of the present application will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present application. It will be apparent that the described embodiments are one embodiment, but not all embodiments, of the present application. All other embodiments, which can be made by a person skilled in the art without creative efforts, based on the described embodiments of the present application fall within the protection scope of the present application.

It is to be noted that unless otherwise defined, technical or scientific terms used herein should be taken in a general sense as understood by one of ordinary skill in the art to which the present application belongs.

In the description of the embodiments of the present application, the meaning of "plurality" is at least two, for example, two, three, etc., unless explicitly defined otherwise.

Referring to fig. 1 and 2, a screw electromagnetic pump 100 according to an embodiment of the present application includes: the pump groove outer housing 20, the pump groove inner housing 10, the pump groove pipe 30, the first helical blade 31, the second helical blade 111, and the electromagnetic driving device.

The pump channel housing 20 defines a receiving chamber 21, the radial peripheral wall 22 of the pump channel housing 20 being provided with a liquid inlet 201 communicating with the receiving chamber 21 for receiving liquid metal. The pump groove inner casing 10 is disposed in the accommodation chamber 21.

Both axial ends of the pump channel pipe 30 are open ends. A portion of the pump channel tube 30 is located within the receiving chamber 21 and another portion extends from one side axial end wall 23 of the pump channel housing 20 to the outside of the receiving chamber 21. An outer annular flow passage 202 is formed between the pump groove pipe 30 and the pump groove outer casing 20, and an inner annular flow passage 102 communicating with the outer annular flow passage 202 is formed between the pump groove pipe 30 and the pump groove inner casing 10, so that the liquid metal entering the accommodating chamber 21 via the liquid flow inlet 201 flows through the outer annular flow passage 202 and the inner annular flow passage 102 in sequence, and flows out from an opening end 301 of the pump groove pipe 30 located outside the accommodating chamber 21.

The open end 301 of the pump channel tube 30, which is located outside the receiving chamber 21, is the fluid outlet of the solenoid pump 100.

The first helical blade 31 is disposed between the pump groove pipe 30 and the pump groove housing 20 to form an outer helical flow passage within the outer annular flow passage 202. The second helical vane 111 is disposed between the pump groove pipe 30 and the pump groove inner housing 10 to form an inner helical flow path within the inner annular flow path 102.

The electromagnetic driving means is used to provide electromagnetic force for driving the liquid metal to flow from the liquid inlet 201 along the outer spiral runner to the inner spiral runner.

In the embodiment of the application, since the inner and outer double-layer spiral flow channels are formed in the pump groove shell 20, when the electromagnetic driving device provides electromagnetic force for driving liquid metal to flow, the lift of the electromagnetic pump is obviously improved compared with that of one spiral channel because the liquid metal is driven by two spiral channels.

In addition, compared with the spiral flow passage with only one layer, the spiral electromagnetic pump 100 according to the embodiment of the application can effectively reduce the volume and weight of the electromagnetic pump, for example, the volume can be reduced by about 50% due to the inner and outer double-layer spiral flow passages formed inside the pump groove housing 20. Meanwhile, the embodiment of the application can also improve the efficiency of the spiral electromagnetic pump 100 by about 28% compared with other types of electromagnetic pumps due to the formation of the inner and outer double-layer spiral flow channels inside the pump groove shell 20.

Referring to fig. 3, in some embodiments, a first helical blade 31 is formed at a radially outer surface of the pump groove conduit 30. In such an embodiment, the first helical blade 31 may be an outer helical groove or an outer helical rib formed in the pump groove conduit 30. The first helical blade 31 extends helically on the pump channel tube 30. It will be readily appreciated that the pitch of the first helical blade 31 is much smaller than the length of the first helical blade 31 in the axial direction. For example, the length of the first helical blade 31 in the axial direction may be 5 times or more the pitch.

In some embodiments, the first helical blades 31 may be in clearance fit with the inner surface of the radial peripheral wall 22 of the pump groove housing 20. Thus, the liquid metal can be effectively prevented from flowing directly through the gap between the radial end of the spiral vane and the radial peripheral wall 22 of the pump groove housing 20 without flowing into the spiral flow passage. The first helical blade 31 may be welded to the radially outer surface of the pump channel tube 30.

In other embodiments, the first helical blades 31 may also be formed on the inner surface of the radial peripheral wall 22 of the pump groove housing 20. The first helical blade 31 may be welded to the inner surface of the radial peripheral wall 22 of the pump groove housing 20.

Referring to fig. 4, in some embodiments, the second helical blades 111 may be formed on the outer surface of the radial peripheral wall of the pump groove inner housing 10. In such an embodiment, the second helical blade 111 may be an outer helical groove or an outer helical rib formed in the radial peripheral wall of the pump groove inner housing 10. The second helical blades 111 extend spirally on the radial peripheral wall of the pump groove inner housing 10. It will be readily appreciated that the pitch of the second helical blade 111 is much smaller than the length of the second helical blade 111 in the axial direction. For example, the length of the second helical blade 111 in the axial direction may be 5 times or more the pitch.

The second helical blade 111 is in clearance fit with the radially inner surface of the pump channel tube 30. Thus, the liquid metal can be effectively prevented from flowing directly through the gap between the radial end of the spiral vane and the wall of the pump channel pipe 30 without flowing into the spiral flow passage. The second helical blades 111 may be welded to the outer surface of the radial peripheral wall of the pump groove inner housing 10.

In other embodiments, the second helical blade 111 may also be formed on the radially inner surface of the pump channel tube 30. The second helical blade 111 may also be welded to the radially inner surface of the pump channel tube 30.

In some embodiments, the pitch of the first helical blade 31 and the second helical blade 111 are the same, thereby maintaining as much as possible stability of the liquid metal flow.

In some embodiments, the first helical blade 31 and the second helical blade 111 are the same length in the axial direction.

In some embodiments, the direction of rotation of the first and second helical blades 31, 111 is reversed, thereby facilitating an increase in the flow rate of the liquid metal. In other embodiments, as shown in fig. 3 and 4, the rotation directions of the first and second helical blades 31 and 111 may be the same.

In some embodiments, the inner annular runner 102 is the same annular width as the outer annular runner 202, thereby helping to maintain stability of the liquid metal flow.

In some embodiments, the annular width of the outer annular flow channel 202 is less than the diameter of the fluid inlet 201. Further, the annular width of the outer annular flow passage 202 is one third to one eighth of the diameter of the liquid flow inlet 201. Thus, when liquid metal flows from the liquid inlet 201 into the outer annular flow channel 202 in the helical flow channel, current can be conducted axially through the turns of liquid metal and the inter-turn helical blades in sequence, so that there is reliable electrical contact between the turns of the liquid metal channel and between the liquid metal and the channel wall, so that secondary current can flow axially through the turns of the channel in sequence.

In some embodiments, a spacing exists between an axial end face 33 of the pump groove conduit 30 within the receiving chamber 21 and the other axial end wall of the pump groove housing 20. The inner annular flow passage 102 communicates with the outer annular flow passage 202 through this spacing.

The spacing between the axial end face 33 of the pump channel tube 30 in the receiving chamber 21 and the axial end wall of the pump channel outer housing 20 on the side adjacent to the axial end face 33 is greater than the spacing between the inner surface of the radial peripheral wall 22 of the pump channel outer housing 20 and the outer surface of the radial peripheral wall of the pump channel inner housing 10 in order to improve the continuity and stability of the liquid metal flow.

In other embodiments, at least one through hole may be provided in the pump channel tube 30 near the axial end face 33 located in the receiving chamber 21, so that the inner annular flow passage 102 and the outer annular flow passage 202 communicate through the at least one through hole.

In some embodiments, one side axial end wall of the pump groove outer housing 20 adjacent to the axial end surface 33 is fixedly connected to an axial end wall of the corresponding side of the pump groove inner housing 10. For example, one side axial end wall of the pump groove outer housing 20 adjacent to the axial end face 33 is welded to the corresponding side axial end wall of the pump groove inner housing 10.

In some embodiments, a portion of one side of the pump groove outer housing 20 adjacent to the axial end face 33 serves as an axial end wall for a corresponding side of the pump groove inner housing 10. That is, the pump groove outer casing 20 shares one side axial end wall with the pump groove inner casing 10. The end face of the radial pipe wall of the pump groove inner casing 10 is welded directly to one side axial end wall of the pump groove outer casing 20.

The fluid inlet 201 may be located away from the axial end face 33 of the pump channel tube 30 within the receiving chamber 21. The length of the spiral flow channel is increased by the arrangement.

The first helical blade 31 may extend from the axial end face 33 of the pump channel tube 30 located in the receiving chamber 21 in the direction of the liquid flow inlet 201.

The pump channel pipe 30 is provided with a plurality of first diversion parts 32 near the radial outer side surface of the liquid inlet 201 at intervals along the circumferential direction, and the liquid metal entering the accommodating cavity 21 through the liquid inlet 201 is diverted through the plurality of first diversion parts 32 and then enters the outer layer spiral flow passage, so that the liquid metal can flow according to the designed spiral flow passage.

The number of the first flow guiding portions 32 may be, for example, 3, 4, 5, or more. The length direction of the first diversion portion 32 forms an angle with the axial direction of the pump channel pipe 30.

The first deflector 32 includes a first sidewall 321, a second sidewall 322 connected to the first sidewall 321, and a connecting sidewall 323 connecting the first sidewall 321 and the second sidewall 322. The first sidewall 321 and the second sidewall 322 are arc-shaped, and the first sidewall 321 and the second sidewall 322 are smoothly transited through the arc-shaped connecting sidewall 323. The arc shape of the first side wall 321 and the arc shape of the second side wall 322 are approximately the same as the spiral direction of the first spiral vane 31, thereby being more beneficial to the liquid metal flowing according to the designed spiral flow channel.

In some embodiments, the pump groove inner housing 10 includes a straight tube section 11 having a uniform inner diameter and a inducer section 12 connected to the straight tube section 11 and having a tapered inner diameter, the inducer section 12 being closer to the fluid inlet 201 of the pump groove outer housing 20 than the straight tube section 11. The flow guiding section 12 can reduce the flow resistance loss.

The second helical blades 111 are formed on the radially outer side surface of the straight pipe section 11.

The radially outer surface of the straight pipe section 11 between the second helical blade 111 and the guide section 12 is provided with a plurality of second guide portions 112 at intervals in the circumferential direction, and the liquid metal flowing out of the outer helical flow passage enters the pump groove pipe 30 after being guided by the plurality of second guide portions 112. The second flow guiding portion 112 may have substantially the same shape as the first flow guiding portion 32, and also has a first side wall, a second side wall connected to the first side wall, and a connecting side wall connecting the first side wall and the second side wall. The arc shape of the first and second sidewalls of the second guide part 112 is substantially the same as the spiral direction of the second spiral vane 111.

In some embodiments, the first helical blade 31, the second helical blade 111 are the same material as the pump channel tube 30. For example, when the operating temperature is below 600 ℃, the first helical blade 31, the second helical blade 111, and the pump channel tube 30 are typically selected from austenitic stainless steel materials.

In some embodiments, the electromagnetic drive apparatus includes: an inner core 40, an outer core 50, and a plurality of coils 60.

The inner core 40 is disposed within the pump groove inner housing 10. In some embodiments, the inner core 40 may be formed by stacking a plurality of silicon steel sheets circumferentially inside the pump groove inner housing 10 in a radial direction. In some embodiments, the inner core 40 may be comprised of a plurality of segmented cores. Each sector iron core is formed by tightly stacking a plurality of silicon steel sheets along the circumferential direction. A support shaft may be provided inside the pump groove inner case 10 for supporting the inner core 40.

The specific form of the inner core 40 is not limited thereto. In other embodiments, the inner core 40 may have other configurations as are commonly used in the art.

The outer core 50 is disposed radially outward of the pump groove housing 20. The outer core 50 may extend axially along the radially outer side of the pump groove housing 20. A plurality of coils 60 are provided to the outer core 50.

In some embodiments, the outer core 50 is provided with a plurality of circumferentially extending winding slots along its length. The winding slots are equally spaced along the length of the outer core 50. Each coil 60 is correspondingly disposed in one winding slot of the outer core 50.

In other embodiments, the outer core 50 is provided with a plurality of axially extending slots along its circumferential direction. Each slot may be formed by recessing downwardly from the upper surface of the outer core 50, with both axial sides of the slot being open ends. A plurality of coils 60 are inserted into each slot, and the coils 60 are distributed along the depth direction of the grooves. In such embodiments, the coil 60 may be removed and installed directly from the slot without cutting the tubing, which may reduce the risk of liquid metal leakage, as well as introduce air impurities into the liquid metal system, contaminating the quality of the liquid metal. Furthermore, this arrangement also facilitates natural ventilation and heat dissipation of the coil 60, i.e., without the need for an additional cooling system.

The sump housing 20 typically also has a higher temperature due to the too high temperature of the liquid metal flowing into the sump housing 20. A thermal barrier 70 may be provided between the outer core 50 and the pump groove housing 20 to block radial heat transfer from the pump groove housing 20 to the outer core 50 to prevent excessive temperatures of the outer core 50 and the coil 60. In some embodiments, the insulation layer 70 may be a short fiber insulation blanket.

Compared with a cylindrical induction type electromagnetic pump, the spiral electromagnetic pump 100 of the embodiment of the application has higher efficiency and smaller volume under the condition of the same flow-lift performance index, and is suitable for occasions with strict restrictions on installation space and efficiency indexes, including nuclear submarines, space piles, small piles and the like.

It should also be noted that, in the embodiments of the present application, the features of the embodiments of the present application and the features of the embodiments of the present application may be combined with each other to obtain new embodiments without conflict.

The present application is not limited to the above embodiments, but the scope of the application is defined by the claims.

Claims

1. A screw electromagnetic pump, comprising:

the pump groove inner shell is arranged in the accommodating cavity;

2. The screw electromagnetic pump of claim 1, wherein the first helical vane is formed on a radially outer surface of the pump groove conduit.

3. The screw electromagnetic pump of claim 2 wherein the first helical vane is in clearance fit with an inner surface of a radial peripheral wall of the pump groove housing.

4. The screw electromagnetic pump of claim 1, wherein the second helical vane is formed on an outer surface of a radial peripheral wall of the pump groove inner housing.

5. The screw electromagnetic pump of claim 4 wherein the second helical vane is in clearance fit with a radially inner surface of the pump groove conduit.

6. The screw electromagnetic pump of claim 1, wherein the first and second screw blades have the same pitch and opposite rotational directions.

7. The screw electromagnetic pump of claim 1 wherein the inner annular flow passage has the same annular width as the outer annular flow passage.

8. The screw electromagnetic pump of claim 7 wherein the annular flow passage has a ring width of one third to one eighth of the diameter of the fluid inlet.

9. The screw electromagnetic pump of claim 1, wherein a spacing exists between an axial end face of the pump channel conduit within the receiving cavity and the other axial end wall of the pump channel housing such that an outer annular flow passage is formed between the pump channel conduit and the pump channel housing and an inner annular flow passage is formed between the pump channel conduit and the pump channel inner housing in communication with the outer annular flow passage.

10. The screw electromagnetic pump of claim 9, wherein a spacing between an axial end face of the pump groove conduit within the receiving cavity and a side axial end wall of the pump groove housing adjacent the axial end face is greater than a spacing between an inner surface of a radial peripheral wall of the pump groove housing and an outer surface of the radial peripheral wall of the pump groove inner housing.

11. The screw electromagnetic pump of claim 9, wherein an axial end wall of one side of the pump groove outer housing adjacent the axial end face is fixedly connected to an axial end wall of a corresponding side of the pump groove inner housing; or (b)

The axial end wall portion of one side of the pump groove outer housing adjacent the axial end face serves as an axial end wall of the corresponding side of the pump groove inner housing.

12. The screw electromagnetic pump of claim 1, wherein the fluid inlet is disposed away from an axial end face of the pump channel conduit within the receiving cavity;

the first helical blade extends from an axial end face of the pump channel tube in the receiving chamber in the direction of the liquid flow inlet.

13. The screw electromagnetic pump according to claim 1, wherein the pump channel pipe is provided with a plurality of first diversion portions at intervals in a circumferential direction near a radially outer side surface of the liquid flow inlet, and the liquid metal entering the accommodating chamber through the liquid flow inlet is diverted through the plurality of first diversion portions and then enters the outer layer screw flow passage.

14. The screw electromagnetic pump of claim 1, wherein the pump groove inner housing comprises a straight tube section with a uniform inner diameter and a diversion section connected with the straight tube section and having a tapered inner diameter, the diversion section being closer to the liquid flow inlet of the pump groove outer housing than the straight tube section;

wherein the second helical blade is formed on a radially outer surface of the straight tube section.

15. The screw electromagnetic pump of claim 14, wherein a radially outer surface of the straight tube section between the second helical vane and the deflector section is provided with a plurality of second deflector portions circumferentially spaced apart, and the liquid metal flowing from the outer helical runner is deflected by the plurality of second deflector portions and then enters the pump groove pipe.

16. The screw electromagnetic pump of claim 1, wherein the electromagnetic drive comprises:

the inner iron core is arranged in the pump ditch inner shell;

an outer core disposed radially outward of the pump groove housing; and

and a plurality of coils disposed on the outer core.

17. The screw electromagnetic pump of claim 16, wherein a thermal insulation layer is disposed between the outer core and the pump groove housing.