CN115007010A - Adjustable throttle high-lift gas-liquid mixing pump - Google Patents
Adjustable throttle high-lift gas-liquid mixing pump Download PDFInfo
- Publication number
- CN115007010A CN115007010A CN202210671651.8A CN202210671651A CN115007010A CN 115007010 A CN115007010 A CN 115007010A CN 202210671651 A CN202210671651 A CN 202210671651A CN 115007010 A CN115007010 A CN 115007010A
- Authority
- CN
- China
- Prior art keywords
- impeller
- liquid
- flow channel
- gas
- outlet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
- B01F25/00—Flow mixers; Mixers for falling materials, e.g. solid particles
- B01F25/60—Pump mixers, i.e. mixing within a pump
- B01F25/64—Pump mixers, i.e. mixing within a pump of the centrifugal-pump type, i.e. turbo-mixers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
- B01F23/00—Mixing according to the phases to be mixed, e.g. dispersing or emulsifying
- B01F23/20—Mixing gases with liquids
-
- 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
- F04D29/2205—Conventional flow pattern
- F04D29/2222—Construction and assembly
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02W—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO WASTEWATER TREATMENT OR WASTE MANAGEMENT
- Y02W10/00—Technologies for wastewater treatment
- Y02W10/10—Biological treatment of water, waste water, or sewage
Abstract
The invention discloses a high-lift gas-liquid mixing pump with adjustable flow rate, which comprises an impeller, a pump body and a main shaft, wherein the impeller is arranged at one end of the main shaft and is positioned in the pump body; the impeller is provided with at least two flow channels with impeller outlet mounting angles, and the difference value of the two outlet mounting angles is more than fifty degrees. The impeller is a cross impeller or a level impeller: the crossed impeller is provided with a liquid flow channel and a gas-liquid flow channel which are alternately distributed on the same cross section of the axis of the impeller, the installation angle of the outlet of the working surface of the liquid flow channel is smaller than that of the outlet of the working surface of the gas-liquid flow channel, and an exchange hole is arranged between the back surface of the liquid flow channel and the working surface of the gas-liquid flow channel; the cascade impeller is provided with a first flow passage and a second flow passage which are positioned on the cross section adjacent to the axis of the impeller, the pump body comprises a volute and an inducer, the first flow passage is closer to the inducer than the second flow passage, and the inducer is provided with a rotational flow structure.
Description
Technical Field
The invention relates to the technical field of gas-liquid mixing pumps, in particular to a gas-liquid mixing pump with adjustable flow and high lift.
Background
The gas-liquid mixing pump is mainly used for fully stirring and mixing gas and liquid and pressurizing and conveying, and main performance parameters comprise a gas-liquid ratio range, a cavitation allowance, a use temperature, a flow delivery lift and the like, wherein the stable work doing of the impeller is adversely affected due to the range change of the gas-liquid mixing ratio and the difference of the gas-liquid mixing distribution state of an initial suction position.
The impeller in the prior art generally adopts the impeller configuration of the traditional centrifugal pump, the specific rotating speed of the impeller is roughly determined by taking the gas-liquid mixing average value of the design working condition as the parameter of a conveying medium, and then final shaping is carried out by only adjusting the wall thickness, the surface roughness and the like of the impeller, therefore, when the gas-liquid mixing ratio deviates from the design value a lot, the setting angle of the impeller blade can not work with the optimal parameter, the lift is reduced very fast, the working efficiency is also influenced greatly, moreover, the gas-liquid mixed medium is only pumped and thrown out simultaneously in the impeller, the kinetic energy is consistent, the outlet speed is also consistent with the gas and the liquid, therefore, the secondary improvement of the uniformity of the gas-liquid mixture in the delivery pump is not obvious, therefore, if the structure of the traditional centrifugal pump is continuously used for gas-liquid mixing and conveying in the prior art, the lift parameters and the gas-liquid mixing quality cannot be fully ensured.
Disclosure of Invention
The invention aims to provide a flow-adjustable high-lift gas-liquid mixing pump to solve the problems in the background technology.
In order to solve the technical problems, the invention provides the following technical scheme:
a high-lift gas-liquid mixing pump with adjustable flow rate comprises an impeller, a pump body and a main shaft, wherein the impeller is arranged at one end of the main shaft and is positioned in the pump body; the impeller is provided with at least two flow channels with impeller outlet mounting angles, and the difference value of the two outlet mounting angles is more than fifty degrees.
The two kinds of outlet placement angles are respectively used for pumping two kinds of media, the outlet placement angle is small and used for pumping pure liquid, the outlet placement angle is large and used for pumping the medium with larger gas content, the two kinds of media can respectively obtain supercharging power by a more proper working surface, and stable gas phase, liquid phase and mixed phase pressure is obtained at the outlet of the impeller, so that the pressure fluctuation of the outlet of the pump is reduced, the pressure of gas and liquid at the outlet of the impeller is mutually matched, so that the mutual stirring and mixing force can be more easily exerted, bubble clusters below the micron level are formed in the liquid, and meanwhile, the mixing and stable supercharging of the gas-liquid mixing pump are guaranteed.
As a further design scheme: the impeller is a crossed impeller, the crossed impeller is provided with a liquid runner and a gas-liquid runner which are alternately distributed on the same cross section of the axis of the impeller, the working surface of the liquid runner is a low-angle working surface, the working surface of the gas-liquid runner is a high-angle working surface, a communicated exchange hole is arranged between the back surface of the liquid runner and the high-angle working surface, the outlet installation angle of the low-angle working surface is lower than that of the high-angle working surface, and the liquid runner occupies the inlet area of the hub of the impeller.
The centrifugal impeller disk surface on the cross section of one shaft is provided with alternate flow channels, the outlet installation angle of the liquid flow channel with a low-angle working surface is small, the centrifugal impeller disk surface is suitable for conveying a medium with large liquid components, the gas-liquid flow channel with a large outlet installation angle is used for increasing the medium containing more gas components, the large outlet installation angle can apply more work to the medium under a limited radial conveying distance to enable the medium to have larger kinetic energy at the outlet, the specific work application ratio can be analyzed by taking a centrifugal impeller speed triangle as a tool, when the impeller is carried out at the initial stage of mixing the medium, the medium firstly and completely enters the liquid flow channel, however, due to the rotation of the impeller, the medium is more tightly attached to the working surface of the liquid flow channel, due to the rotation inertia, pure liquid components with small bubble content are accumulated near the surface of the low-angle working surface and advance along the low-angle working surface, and mixed components with large bubble content enter the gas-liquid flow channel from an exchange hole, the high-angle working face receives power transmitted by the impeller to improve self kinetic energy and pressure, the two strands of media thrown out of the gas-liquid flow channel and the liquid flow channel are identical in radial position but different in absolute speed direction, the gas-liquid mixture has larger absolute speed and collides with pure liquid media just out of the impeller along different directions, the gas-liquid mixing effect is better, and the uniformity of the final mixture and the gas-liquid pressure matching degree are better.
Furthermore, a flow blocking area is arranged between the back face and the high-angle working face of the crossed impeller, the flow blocking area is filled with a flow passing area of the liquid flow channel and the gas-liquid flow channel at the radial outlet position of the crossed impeller, and the flow passing area of the liquid flow channel is gradually reduced.
The flow blocking area is a solid structure or a semi-hollow structure which is outward in the radial direction, in a word, the flow blocking area cannot become an overflowing part of a liquid flow channel and a gas-liquid flow channel, the width of the flow channel of the liquid flow channel is basically unchanged, the overflowing area is also related to the height of the flow channel surrounded by front and rear cover plates of the impeller, the overflowing area of the liquid flow channel is constructed to be in a state of gradually reducing along an overflowing path, part of gas-liquid medium can be forced to enter the gas-liquid flow channel at the position of an exchange hole to cause inevitable shunting of two kinds of medium, one strand with large bubble content is selected to be extruded into the gas-liquid flow channel to be subjected to larger work power, and inevitable impact mixing is formed at the outlet of the crossed impeller.
As another further design scheme: the impeller is a hierarchical impeller, the hierarchical impeller is provided with a first flow channel and a second flow channel which are positioned on the adjacent cross section of the axis of the impeller, the pump body comprises a volute and an inducer, the first flow channel is closer to the inducer than the second flow channel, the inlet of the first flow channel is a first inlet, the inlet of the second flow channel is a second inlet, the first inlet radially surrounds the second inlet, the inducer is provided with a rotational flow structure, and the placement angle of the blade outlet in the first flow channel is smaller than that of the blade outlet in the second flow channel.
The level impeller is respectively used as two layers of flow channels to do work on a medium entering the level impeller, the medium entering the pump body is swirled by the inlet section to distribute pure liquid on the outer layer, a gas-liquid mixture is distributed at the central position, the gas-liquid mixture enters the second flow channel and is swung by the blades with larger outlet placement angles to obtain larger single-stage power, the pure liquid enters the first flow channel and is swung by the traditional centrifugal blades with small outlet placement angles to do work, and the pure liquid does not enter the second flow channel to prevent the blades with large placement angles from swinging the pure liquid to enable the driving power required by the impeller to sharply rise.
Further, the cyclone structure is a swirler which is rotatably supported by a support extending from the inner wall of the inlet section, and the swirler is a helical blade.
The helical blades can make the medium entering the pump body rotate actively, passively or even not, a certain peripheral speed can be given as long as the medium passes through the swirler, and pure liquid is distributed on the outer layer of the inlet section and advances to the first inlet to enter the first flow channel.
Furthermore, the swirler includes first spiral shell leaf, second spiral shell leaf and reversal transmission, and first spiral shell leaf and second spiral shell leaf are rotatory respectively to be supported and install in the inlet section, and first spiral shell leaf and second spiral shell leaf axis coincide and the rotation axis is close to one end each other and is connected through reversal transmission.
The two spiral blades rotate in different rotating directions, after the first spiral blade divides the medium into two streams which respectively enter the first flow channel and the second flow channel, the medium circumferential speed is eliminated by the reverse rotation of the second spiral blade, and the medium only has axial speed when entering the two flow channels, so that the single-stage acting capacity of the blade is prevented from being seriously influenced by the triangular deformation of the inlet speed of the blade.
Further, the reverse rotation transmission comprises a first inner gear, a second inner gear, a first matching wheel, a second matching wheel and a matching wheel center frame, the first inner gear is fixed at the end part of a rotating shaft of the first spiral blade, the second inner gear is fixed at the end part of the rotating shaft of the second spiral blade, the first inner gear and the second inner gear are arranged in a face-to-face mode, the first matching wheel is provided with two outer gears distributed on the rotating shaft, one of the two outer gears of the first matching wheel is meshed with the first inner gear, the second matching wheel is provided with two outer gears distributed on the rotating shaft, one of the two outer gears of the second matching wheel is meshed with the second inner gear, the first matching wheel and the second matching wheel are meshed with the remaining outer gear, and the rotating shafts of the first matching wheel and the second matching wheel are rotatably supported by the matching wheel center frame and keep the center distance.
The transmission path from the first spiral blade rotating shaft to the second spiral blade rotating shaft has three transmission positions, the meshing of the inner gear and the outer gear at two positions does not change the steering direction, the meshing of the outer gear at one position changes the steering direction, and the steering time of the first spiral blade and the steering time of the second spiral blade are kept opposite.
Furthermore, the level impeller also comprises a detachable annular nozzle arranged at the radial outlet, and the radial dimension of the side of the annular nozzle connected with the second flow passage is larger than that of the side of the annular nozzle connected with the first flow passage.
The removable interchangeable of ring mouth can regard as the extension section of first runner and second runner, continues to do work for the medium in two runners, and the export lay angle can further selectivity adjustment, and it should be noted that, mainly adjusts the export lay angle of gas-liquid mixture place runner, does not propose to do great degree adjustment to the export lay angle of pure liquid medium, because the spiral case need adapt to the angle of effluence of this kind of high density medium of liquid, prevents that the angle is not suitable and takes place liquid striking spiral case wall.
Furthermore, the two outlet installation angles arranged on the impeller are respectively a backward inclination installation angle and a forward inclination installation angle.
The two blade placement angles are respectively inclined backwards and forwards at the outlet position, the left inclined backwards blade is used for liquid conveying, the right inclined forwards provides more single-stage power for gas-liquid mixture without worrying about power overload of a main shaft, the absolute speed of the medium outlet of the forward inclined blade is higher and is different from the speed and angle of the liquid outlet of the adjacent inclined backwards blade, and two media are fully mixed in a crossed mode at the outlet position and flow out from the outlet of the pump body.
Compared with the prior art, the invention has the following beneficial effects: the invention constructs two independent flow channels at the impeller position to pertinently convey gas-liquid mixed media which are not dispersed and distributed, so that components with more water content enter the flow channel with a small outlet placement angle, the working efficiency is ensured, the overpower is prevented, the components with more gas content enter the flow channel with a large outlet placement angle, the medium in the flow channel can be worked with higher power, and because the gas content is more, the rapid rise of the power of the impeller is not needed to be worried about, the two flow passages respectively do work, the outlet of the impeller has different outlet speed directions, the outlet speed directions are mutually sheared, the gas component is collided into the liquid component by larger kinetic energy and is dispersed to form a running gas-liquid mixed phase, the separated working flow passages can respectively keep higher conversion efficiency by a more proper working surface shape to obtain stable high lift, and the flow is adjusted by the inlet section entering resistance or the change of the rotating speed of the main shaft.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the principles of the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic cross-sectional view of an impeller according to a first embodiment of the present invention;
FIG. 2 is view A of FIG. 1;
FIG. 3 is a schematic structural diagram of a second embodiment of the present invention;
FIG. 4 is a schematic axial view of a second impeller according to an embodiment of the present invention;
FIG. 5 is a schematic view of a two-layer blade shape for a two-impeller cross-sectional configuration in accordance with an embodiment of the present invention;
FIG. 6 is a schematic view of a structure relating to the position of a second swirler in accordance with an embodiment of the present invention;
FIG. 7 is a schematic structural view of a second counter-rotating drive according to an embodiment of the present invention;
in the figure: the device comprises a 1-crossed impeller, a 11-liquid flow channel, a 12-gas-liquid flow channel, a 13-exchange hole, a 14-flow blocking area, a 101-low-angle working surface, a 102-back surface, a 103-high-angle working surface, a 2-level impeller, a 21-first flow channel, a 211-first inlet, a 22-second flow channel, a 221-second inlet, a 23-annular nozzle, a 3-pump body, a 31-volute, a 32-inlet section, a 4-cyclone, a 41-first spiral blade, a 42-second spiral blade, a 43-reverse transmission, a 431-first internal gear, a 432-second internal gear, a 433-first matching wheel, a 434-second matching wheel, a 435-matching wheel center frame and a 5-main shaft.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The first embodiment is as follows: referring to fig. 1-2, the present invention provides a technical solution:
a adjustable throttle high-lift gas-liquid mixing pump comprises an impeller, a pump body 3 and a main shaft 5, wherein the impeller is arranged at one end of the main shaft 5 and is positioned in the pump body 3;
the impeller is provided with at least two flow channels of impeller outlet installation angles, and the difference value of the two outlet installation angles is more than fifty degrees.
The two outlet installation angles are respectively used for pumping two types of media, the outlet installation angle is small and used for pumping pure liquid, the outlet installation angle is large and used as a medium with larger gas content, the two types of media can respectively obtain supercharging power by a more proper working surface, and stable gas phase, liquid phase and mixed phase pressure is obtained at the outlet of the impeller, so that the pressure fluctuation of the outlet of the pump is reduced, the pressure of the gas and the pressure of the liquid at the outlet of the impeller are mutually matched, so that the mutual stirring and mixing force can be more easily applied, bubble clusters below micron-level are formed in the liquid, and meanwhile, the mixing and stable supercharging of the gas-liquid mixing pump are ensured.
The impeller is a crossed impeller 1, the crossed impeller 1 is provided with a liquid flow passage 11 and a gas-liquid flow passage 12 which are alternately distributed on the same cross section of the axis of the impeller, the working surface of the liquid flow passage 11 is a low-angle working surface 101, the working surface of the gas-liquid flow passage 12 is a high-angle working surface 103, a communicated exchange hole 13 is arranged between the back surface 102 of the liquid flow passage 11 and the high-angle working surface 103, the outlet installation angle of the low-angle working surface 101 is lower than that of the high-angle working surface 103, and the liquid flow passage 11 occupies the inlet area of the whole impeller hub.
As shown in figures 1 and 2, the centrifugal impeller disk surface on one axial cross section is provided with alternate flow channels, the liquid flow channel 11 with the low-angle working surface 101 has a small outlet installation angle and is suitable for conveying a medium with a large liquid component, the gas-liquid flow channel 12 with a large outlet installation angle is used for increasing the medium with more gas components, the large outlet installation angle can apply more work to the medium under a limited radial conveying distance to enable the medium to have larger kinetic energy at the outlet, the specific work comparison can be analyzed by taking a centrifugal impeller speed triangle as a tool, when the impeller is carried out at the initial stage of mixing the medium, the medium firstly and completely enters the liquid flow channel 11, however, due to the rotation of the impeller, the medium is more tightly attached to the working surface of the liquid flow channel 11, and due to the rotation inertia, the pure liquid component with less bubble content is accumulated near the surface of the low-angle working surface 101 and advances along the low-angle working surface 101, the mixed components with more bubble content enter the gas-liquid flow channel from the exchange hole 13, the power transmitted by the impeller is received on the high-angle working surface 103 to improve the self kinetic energy and pressure, the radial positions of the two strands of media thrown out from the gas-liquid flow channel 12 and the liquid flow channel 11 are the same, but the absolute speed directions are different, the gas-liquid mixture has larger absolute speed and collides with the pure liquid medium just out of the impeller along different directions, the gas-liquid mixing effect is better, and the uniformity of the final mixture and the gas-liquid pressure matching degree are better.
The cross impeller 1 is provided with a flow blocking area 14 between the back surface 102 and the high-angle working surface 103, the flow blocking area 14 fills the flow passing areas of the liquid flow channel 11 and the gas-liquid flow channel 12 at the radial outlet position of the cross impeller 1, and the flow passing area of the liquid flow channel 11 is gradually reduced.
As shown in fig. 1, the flow blocking region 14 is a solid structure or a semi-hollow structure radially outward, and in short, cannot be an overflowing portion of the liquid flow channel 11 and the gas-liquid flow channel 12, the overflowing area of the liquid flow channel 11 is basically unchanged in a view of fig. 1, the overflowing area is also related to the height of a flow channel enclosed by front and rear cover plates of the impeller, the overflowing area of the liquid flow channel 11 is gradually reduced along an overflowing path, a part of the gas-liquid medium can be forced into the gas-liquid flow channel 12 at the position of the exchange hole 14, so that two streams of the medium are inevitably shunted, and one stream with a large bubble content is selected to be extruded into the gas-liquid flow channel 12 to receive a larger acting power, and inevitable impact mixing is formed at the outlet of the cross impeller 1.
The two outlet mounting angles arranged on the impeller are respectively a backward tilting mounting angle and a forward tilting mounting angle.
As shown in figure 5, the two blade installation angles are respectively backward inclined and forward inclined at the outlet position, the left backward inclined blade is used for liquid delivery, the right forward inclined blade is used for providing more single-stage power for the gas-liquid mixture without worrying about power overload of the main shaft 5, the absolute speed of the medium outlet of the forward inclined blade is higher and is different from the speed angle of the liquid outlet of the adjacent backward inclined blade, and the two media are fully mixed in a cross way at the outlet position and flow out from the outlet of the pump body 3.
The second embodiment is as follows: referring to fig. 3-7, the present invention provides the following technical solutions:
compared with the first concrete implementation mode, the impeller configuration and the pump body front section leading-in structure are different, the adjustable-throttle high-lift gas-liquid mixing pump comprises an impeller, a pump body 3 and a main shaft 5, wherein the impeller is installed at one end of the main shaft 5 and is positioned in the pump body 3; the impeller is provided with at least two flow channels with impeller outlet mounting angles, and the difference value of the two outlet mounting angles is more than fifty degrees.
The impeller is a level impeller 2, the level impeller 2 is provided with a first flow passage 21 and a second flow passage 22 which are positioned on the adjacent cross sections of the impeller axis, the pump body 3 comprises a volute 31 and an inlet section 32, the first flow passage 21 is closer to the inlet section 32 than the second flow passage 22, the inlet of the first flow passage 21 is a first inlet 211, the inlet of the second flow passage 22 is a second inlet 221, the first inlet 211 radially surrounds the second inlet 221, the inlet section 32 is provided with a rotational flow structure,
the vane exit placement angle in the first flow path 21 is less than the vane exit placement angle of the second flow path 22.
As shown in fig. 3-5, the hierarchical impeller 2 is used as two layers of flow channels to apply work to the medium entering the hierarchical impeller 2, the inlet section 32 swirls the medium entering the pump body 3 to distribute pure liquid on the outer layer, the gas-liquid mixture is distributed on the center position, the gas-liquid mixture enters the second flow channel 22 and is swung by the blades with larger outlet placement angles, so that larger single-stage power is obtained, the pure liquid enters the first flow channel 21 and is swung by the centrifugal blades with the traditional small outlet placement angles to apply work, and the pure liquid should not enter the second flow channel 22 to prevent the blades with large placement angles from swinging the pure liquid, so that the driving power required by the impeller is increased rapidly.
The cyclone structure is a swirler 4, the swirler 4 is rotatably supported by a bracket extending from the inner wall of the inducer 32, and the swirler 4 is a helical blade.
The helical blades can rotate actively, passively or even non-rotatably, and the medium entering the pump body can be given a certain peripheral speed as long as it passes through the swirler 4, and the pure liquid is distributed to the outer layer of the inlet section 32 and advances to the first inlet 211 to enter the first flow channel 21.
The swirler 4 includes a first screw blade 41, a second screw blade 42 and a reverse transmission 43, the first screw blade 41 and the second screw blade 42 are respectively rotatably supported and installed in the inlet section 32, and the ends of the first screw blade 41 and the second screw blade 42, which have the axes coincident and the rotation axes close to each other, are connected by the reverse transmission 43.
As shown in fig. 6, the two blades rotate in different rotation directions, after the first blade 41 has divided the medium into two streams entering the first flow channel 21 and the second flow channel 22, the reverse rotation of the second blade 42 eliminates the circumferential velocity of the medium, so that the medium enters the two flow channels with only axial velocity, thereby preventing the single-stage work-doing capability of the blade from being seriously affected by the triangular deformation of the inlet velocity of the blade.
The reverse gear 43 includes a first internal gear 431, a second internal gear 432, a first engaging wheel 433, a second engaging wheel 434 and an engaging wheel center frame 435, wherein the first internal gear 431 is fixed at the end of the rotating shaft of the first screw blade 41, the second internal gear 432 is fixed at the end of the rotating shaft of the second screw blade 42, the first internal gear 431 and the second internal gear 432 are arranged face to face, the first engaging wheel 433 has two external gears distributed on the rotating shaft, one of the two external gears of the first engaging wheel 433 is engaged with the first internal gear 431, the second engaging wheel 434 has two external gears distributed on the rotating shaft, one of the two external gears of the second engaging wheel 434 is engaged with the second internal gear 432, the remaining one of the first engaging wheel 433 and the second engaging wheel 434 is engaged with each other, and the rotating shafts of the first engaging wheel 433 and the second engaging wheel 435 are rotatably supported by the engaging wheel center frame and maintain the center distance.
As shown in fig. 7, the transmission path from the rotating shaft of the first screw blade 41 to the rotating shaft of the second screw blade 42 has three transmission positions, two positions are meshed with the internal and external gears without changing the rotation direction, one position is meshed with the external gear to change the rotation direction, and the rotation time of the first screw blade 41 is opposite to that of the second screw blade 42.
The stage impeller 2 further comprises a removable annular mouth 23 arranged at the radial outlet, the annular mouth 23 being connected to the second flow channel 22 by a side having a radial dimension greater than that of the side connected to the first flow channel 21.
As shown in fig. 4, the ring mouth 23 is detachable and replaceable, and can be used as an extension section of the first flow channel 21 and the second flow channel 22 to continue to work for the media in the two flow channels, and the outlet setting angle can be further selectively adjusted, it should be noted that the outlet setting angle of the flow channel where the gas-liquid mixture is located is mainly adjusted, and the outlet setting angle for pure liquid media is not recommended to be adjusted to a greater extent, because the volute 31 needs to adapt to the outflow angle of high-density media, such as liquid, so as to prevent the liquid from impacting the wall surface of the volute due to the improper angle.
It is noted that, herein, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Also, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus.
Finally, it should be noted that: although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that changes may be made in the embodiments and/or equivalents thereof without departing from the spirit and scope of the invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (9)
1. The utility model provides an adjustable throttle high-lift gas-liquid mixing pump which characterized in that: the mixing pump comprises an impeller, a pump body (3) and a main shaft (5), wherein the impeller is arranged at one end of the main shaft (5) and is positioned in the pump body (3);
the impeller is provided with at least two flow channels with impeller outlet mounting angles, and the difference value of the two outlet mounting angles is more than fifty degrees.
2. The adjustable flow high-lift gas-liquid mixing pump according to claim 1, characterized in that: the impeller is a crossed impeller (1), the crossed impeller (1) is provided with a liquid flow channel (11) and a gas-liquid flow channel (12) which are alternately distributed on the same cross section of the axis of the impeller, the working surface of the liquid flow channel (11) is a low-angle working surface (101), the working surface of the gas-liquid flow channel (12) is a high-angle working surface (103), exchange holes (13) communicated with the back surface (102) of the liquid flow channel (11) and the high-angle working surface (103) are formed in the middle, the outlet installation angle of the low-angle working surface (101) is lower than that of the high-angle working surface (103), and the liquid flow channel (11) occupies the inlet area of all impeller hubs.
3. The adjustable throttle high-lift gas-liquid mixing pump of claim 2, characterized in that: the cross impeller (1) is provided with a flow blocking area (14) between the back surface (102) and the high-angle working surface (103), the flow blocking area (14) is filled with a liquid flow channel (11) and a gas-liquid flow channel (12) in an overflowing area at the radial outlet position of the cross impeller (1), and the overflowing area of the liquid flow channel (11) is gradually reduced.
4. The adjustable flow high-lift gas-liquid mixing pump according to claim 1, characterized in that: the impeller is a hierarchical impeller (2), the hierarchical impeller (2) is provided with a first flow passage (21) and a second flow passage (22) which are positioned on the adjacent cross sections of the axis of the impeller, the pump body (3) comprises a volute (31) and an inlet section (32), the first flow passage (21) is closer to the inlet section (32) than the second flow passage (22), the inlet of the first flow passage (21) is a first inlet (211), the inlet of the second flow passage (22) is a second inlet (221), the first inlet (211) radially surrounds the second inlet (221), and the inlet section (32) is provided with a rotational flow structure,
the blade outlet setting angle in the first flow passage (21) is smaller than that of the second flow passage (22).
5. The adjustable throttle high-lift gas-liquid mixing pump according to claim 4, characterized in that: the cyclone structure is a cyclone (4), the cyclone (4) is rotatably supported by a bracket extending from the inner wall of the inlet section (32), and the cyclone (4) is a helical blade.
6. The adjustable throttle high-lift gas-liquid mixing pump according to claim 5, characterized in that: the cyclone (4) comprises a first spiral blade (41), a second spiral blade (42) and a reverse transmission (43), the first spiral blade (41) and the second spiral blade (42) are respectively rotatably supported and installed in the inlet section (32), the axes of the first spiral blade (41) and the second spiral blade (42) are overlapped, and the ends, close to each other, of the rotating shafts are connected through the reverse transmission (43).
7. The adjustable flow high-lift gas-liquid mixing pump according to claim 6, characterized in that: the reverse transmission (43) comprises a first inner gear (431), a second inner gear (432), a first matching wheel (433), a second matching wheel (434) and a matching wheel center frame (435), wherein the first inner gear (431) is fixed at the rotating shaft end part of the first screw blade (41), the second inner gear (432) is fixed at the rotating shaft end part of the second screw blade (42), the first inner gear (431) and the second inner gear (432) are arranged in a face-to-face manner, the first matching wheel (433) is provided with two outer gears distributed on the rotating shaft, one of the two outer gears of the first matching wheel (433) is meshed with the first inner gear (431), the second matching wheel (434) is provided with two outer gears distributed on the rotating shaft, one of the two outer gears of the second matching wheel (434) is meshed with the second inner gear (432), and the remaining outer gears of the first matching wheel (433) and the second matching wheel (434) are meshed with each other, the rotating shafts of the first matching wheel (433) and the second matching wheel (434) are rotatably supported by a matching wheel center frame (435) and keep the center distance.
8. The adjustable throttle high-lift gas-liquid mixing pump according to claim 4, characterized in that: the level impeller (2) further comprises a detachable annular nozzle (23) arranged at the radial outlet, and the radial dimension of the side, connected with the second flow passage (22), of the annular nozzle (23) is larger than that of the side, connected with the first flow passage (21), of the annular nozzle.
9. The adjustable flow high-lift gas-liquid mixing pump according to claim 1, characterized in that: the two outlet mounting angles arranged on the impeller are respectively a backward tilting mounting angle and a forward tilting mounting angle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210671651.8A CN115007010B (en) | 2022-06-14 | 2022-06-14 | High-lift gas-liquid mixing pump capable of adjusting flow |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210671651.8A CN115007010B (en) | 2022-06-14 | 2022-06-14 | High-lift gas-liquid mixing pump capable of adjusting flow |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115007010A true CN115007010A (en) | 2022-09-06 |
| CN115007010B CN115007010B (en) | 2023-08-08 |
Family
ID=83074174
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210671651.8A Active CN115007010B (en) | 2022-06-14 | 2022-06-14 | High-lift gas-liquid mixing pump capable of adjusting flow |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115007010B (en) |
Citations (25)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1113551A (en) * | 1995-06-02 | 1995-12-20 | 北京矿冶研究总院 | Centrifugal pulp pump impeller |
| JP2001082384A (en) * | 1999-09-20 | 2001-03-27 | Sanyo Electric Co Ltd | Impeller and centrifugal blower with the impeller |
| US20030231959A1 (en) * | 2002-06-12 | 2003-12-18 | William Hackett | Impeller assembly for centrifugal pumps |
| US20050280167A1 (en) * | 2004-06-21 | 2005-12-22 | Hills Blair H | Apparatus and method for diffused aeration |
| RU69941U1 (en) * | 2007-09-03 | 2008-01-10 | Олег Гедалиевич Деснер | MULTI-STAGE AXIAL PUMP |
| JP3147825U (en) * | 2008-11-04 | 2009-01-22 | サンエー工業株式会社 | Low water level drainage pump |
| CN101653706A (en) * | 2009-08-12 | 2010-02-24 | 华东理工大学 | Circumferential direction mixer and gas-liquid/liquid-liquid mixing method using the same |
| WO2010046993A1 (en) * | 2008-10-24 | 2010-04-29 | 本多機工株式会社 | Volute pump for gas/liquid mixture and microbubble generation device using the same |
| CN201470332U (en) * | 2009-09-09 | 2010-05-19 | 吐哈石油勘探开发指挥部工程技术研究院 | Liquid pipeline blender |
| JP2011153524A (en) * | 2010-01-25 | 2011-08-11 | Panasonic Electric Works Co Ltd | Gas-liquid fluid mixture force feed device |
| CN102889190A (en) * | 2012-10-24 | 2013-01-23 | 徐州五洋科技股份有限公司 | Mining emulsified liquid pump capable of automatically preparing emulsified liquid |
| CN103104547A (en) * | 2013-03-07 | 2013-05-15 | 江苏大学 | Hydraulic unequal pump lift design method for gas-liquid two-phase nuclear main pump impeller |
| CN103104548A (en) * | 2013-03-07 | 2013-05-15 | 江苏大学 | Hydraulic unequal pump lift design method for gas-liquid two-phase nuclear main pump impeller |
| CN203803398U (en) * | 2014-03-03 | 2014-09-03 | 上海维埃姆环保科技有限公司 | Micro gas-liquid mixing pump |
| JP2014217803A (en) * | 2013-05-08 | 2014-11-20 | 株式会社ワイビーエム | Device for and method of generating fine bubble |
| CN105056779A (en) * | 2015-08-28 | 2015-11-18 | 浙江工业大学 | Double rotational flow type oil and gas mixer |
| WO2018117040A1 (en) * | 2016-12-19 | 2018-06-28 | オオノ開發株式会社 | Device and system for generating gas-liquid containing microbubbles |
| CN207598568U (en) * | 2017-12-16 | 2018-07-10 | 山东双轮股份有限公司 | The centrifugal pump impeller of equalization fluid pressure and flow velocity |
| CN208727200U (en) * | 2018-07-25 | 2019-04-12 | 上海尼可尼流体系统有限公司 | Liqiud-gas mixing device |
| CN209195729U (en) * | 2018-10-31 | 2019-08-02 | 广东名航环保技术有限公司 | A kind of self-priming gas energy-saving gas-liquid mixed centrifugal pump |
| CN211259036U (en) * | 2019-09-10 | 2020-08-14 | 浙江南元泵业有限公司 | Asymmetric impeller pump body of gas-liquid mixing pump |
| CN211677236U (en) * | 2020-02-18 | 2020-10-16 | 马世强 | Sleeve mixer |
| CN112370980A (en) * | 2020-11-19 | 2021-02-19 | 太仓中新宝智能装备有限公司 | High-performance gas-liquid mixing device and working method thereof |
| CN113417857A (en) * | 2021-07-02 | 2021-09-21 | 荏原机械淄博有限公司 | Volute type large-flow high-lift wear-resistant middle-open type multi-stage pump |
| US20220258111A1 (en) * | 2019-11-22 | 2022-08-18 | Julián MARTÍNEZ FONSECA | Device for the gasification, pumping and mixing of fluids |
-
2022
- 2022-06-14 CN CN202210671651.8A patent/CN115007010B/en active Active
Patent Citations (25)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1113551A (en) * | 1995-06-02 | 1995-12-20 | 北京矿冶研究总院 | Centrifugal pulp pump impeller |
| JP2001082384A (en) * | 1999-09-20 | 2001-03-27 | Sanyo Electric Co Ltd | Impeller and centrifugal blower with the impeller |
| US20030231959A1 (en) * | 2002-06-12 | 2003-12-18 | William Hackett | Impeller assembly for centrifugal pumps |
| US20050280167A1 (en) * | 2004-06-21 | 2005-12-22 | Hills Blair H | Apparatus and method for diffused aeration |
| RU69941U1 (en) * | 2007-09-03 | 2008-01-10 | Олег Гедалиевич Деснер | MULTI-STAGE AXIAL PUMP |
| WO2010046993A1 (en) * | 2008-10-24 | 2010-04-29 | 本多機工株式会社 | Volute pump for gas/liquid mixture and microbubble generation device using the same |
| JP3147825U (en) * | 2008-11-04 | 2009-01-22 | サンエー工業株式会社 | Low water level drainage pump |
| CN101653706A (en) * | 2009-08-12 | 2010-02-24 | 华东理工大学 | Circumferential direction mixer and gas-liquid/liquid-liquid mixing method using the same |
| CN201470332U (en) * | 2009-09-09 | 2010-05-19 | 吐哈石油勘探开发指挥部工程技术研究院 | Liquid pipeline blender |
| JP2011153524A (en) * | 2010-01-25 | 2011-08-11 | Panasonic Electric Works Co Ltd | Gas-liquid fluid mixture force feed device |
| CN102889190A (en) * | 2012-10-24 | 2013-01-23 | 徐州五洋科技股份有限公司 | Mining emulsified liquid pump capable of automatically preparing emulsified liquid |
| CN103104548A (en) * | 2013-03-07 | 2013-05-15 | 江苏大学 | Hydraulic unequal pump lift design method for gas-liquid two-phase nuclear main pump impeller |
| CN103104547A (en) * | 2013-03-07 | 2013-05-15 | 江苏大学 | Hydraulic unequal pump lift design method for gas-liquid two-phase nuclear main pump impeller |
| JP2014217803A (en) * | 2013-05-08 | 2014-11-20 | 株式会社ワイビーエム | Device for and method of generating fine bubble |
| CN203803398U (en) * | 2014-03-03 | 2014-09-03 | 上海维埃姆环保科技有限公司 | Micro gas-liquid mixing pump |
| CN105056779A (en) * | 2015-08-28 | 2015-11-18 | 浙江工业大学 | Double rotational flow type oil and gas mixer |
| WO2018117040A1 (en) * | 2016-12-19 | 2018-06-28 | オオノ開發株式会社 | Device and system for generating gas-liquid containing microbubbles |
| CN207598568U (en) * | 2017-12-16 | 2018-07-10 | 山东双轮股份有限公司 | The centrifugal pump impeller of equalization fluid pressure and flow velocity |
| CN208727200U (en) * | 2018-07-25 | 2019-04-12 | 上海尼可尼流体系统有限公司 | Liqiud-gas mixing device |
| CN209195729U (en) * | 2018-10-31 | 2019-08-02 | 广东名航环保技术有限公司 | A kind of self-priming gas energy-saving gas-liquid mixed centrifugal pump |
| CN211259036U (en) * | 2019-09-10 | 2020-08-14 | 浙江南元泵业有限公司 | Asymmetric impeller pump body of gas-liquid mixing pump |
| US20220258111A1 (en) * | 2019-11-22 | 2022-08-18 | Julián MARTÍNEZ FONSECA | Device for the gasification, pumping and mixing of fluids |
| CN211677236U (en) * | 2020-02-18 | 2020-10-16 | 马世强 | Sleeve mixer |
| CN112370980A (en) * | 2020-11-19 | 2021-02-19 | 太仓中新宝智能装备有限公司 | High-performance gas-liquid mixing device and working method thereof |
| CN113417857A (en) * | 2021-07-02 | 2021-09-21 | 荏原机械淄博有限公司 | Volute type large-flow high-lift wear-resistant middle-open type multi-stage pump |
Non-Patent Citations (1)
| Title |
|---|
| 王秀勇等: "多级旋涡泵内部流动特性与压力脉动的数值分析", 《排灌机械工程学报》, vol. 34, no. 10, pages 853 - 859 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN115007010B (en) | 2023-08-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101865160B (en) | Partial emission pump with low specific speed | |
| CN104085054B (en) | The closeest, kneading blending and modifying preparation facilities | |
| CN105041720A (en) | Hydraulic design method for efficient and large-flow vortex pump quasi-annulus pumping chamber | |
| CN108547794A (en) | A kind of fire-fighting high-speed centrifugal pump | |
| CN115007010A (en) | Adjustable throttle high-lift gas-liquid mixing pump | |
| CN206071889U (en) | A kind of low noise self-priming combination pump | |
| CN207349169U (en) | A kind of compact liquefied natural gas immersed pump guide vane structure | |
| CN111535974A (en) | Low-water-head large-flow mixed-flow water turbine with double-inlet volute | |
| CN115045991B (en) | Multi-stage gear reducer for hoisting protection | |
| CN207187872U (en) | A kind of grinder of new structure | |
| CN101027493A (en) | Centrifugal impeller and pump apparatus | |
| CN210178642U (en) | Industrial corrosion-resistant self-priming pump impeller | |
| JP4322986B2 (en) | Pump turbine | |
| CN115479019A (en) | Large flow deep well pump | |
| CN105275884B (en) | The enhancing and its application of dynamical type leaf pump | |
| CN210905722U (en) | Static mixing tube | |
| CN210248021U (en) | Impeller for oxygenation pump | |
| CN113790160A (en) | Turbine pump | |
| US2460122A (en) | Pump | |
| CN201433900Y (en) | High abrasion-resistant non-clogging pump | |
| CN211314651U (en) | Hydraulic structure of side runner pump body | |
| CN216381965U (en) | Twisted type uniform-thickness blade and centrifugal wind wheel with same | |
| CN215633957U (en) | Reinforced plastic impeller | |
| CN110748504A (en) | Hydraulic structure of side runner pump body | |
| CN2103038U (en) | Small flow supper low-rate revolution impeller |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |