CN116221058A - Melt pump for conveying high-temperature high-pressure high-viscosity medium - Google Patents
Melt pump for conveying high-temperature high-pressure high-viscosity medium Download PDFInfo
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- CN116221058A CN116221058A CN202310498576.4A CN202310498576A CN116221058A CN 116221058 A CN116221058 A CN 116221058A CN 202310498576 A CN202310498576 A CN 202310498576A CN 116221058 A CN116221058 A CN 116221058A
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- 238000010438 heat treatment Methods 0.000 claims abstract description 41
- 239000000155 melt Substances 0.000 claims abstract description 24
- 238000007599 discharging Methods 0.000 claims abstract description 22
- 238000000034 method Methods 0.000 claims description 13
- 238000004321 preservation Methods 0.000 claims description 9
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 8
- 229910002804 graphite Inorganic materials 0.000 claims description 8
- 239000010439 graphite Substances 0.000 claims description 8
- 230000033001 locomotion Effects 0.000 claims description 6
- 230000008569 process Effects 0.000 claims description 6
- 238000012856 packing Methods 0.000 claims description 5
- 230000017525 heat dissipation Effects 0.000 claims description 2
- 238000003780 insertion Methods 0.000 claims 1
- 230000037431 insertion Effects 0.000 claims 1
- 230000009467 reduction Effects 0.000 abstract description 2
- 238000001125 extrusion Methods 0.000 abstract 1
- 238000009434 installation Methods 0.000 description 9
- 230000000694 effects Effects 0.000 description 7
- 230000002146 bilateral effect Effects 0.000 description 6
- 238000007789 sealing Methods 0.000 description 6
- 230000008901 benefit Effects 0.000 description 4
- 239000000945 filler Substances 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 229910001315 Tool steel Inorganic materials 0.000 description 1
- 238000007792 addition Methods 0.000 description 1
- 230000004075 alteration Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000002457 bidirectional effect Effects 0.000 description 1
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- 229910052804 chromium Inorganic materials 0.000 description 1
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- 238000004891 communication Methods 0.000 description 1
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- 230000003068 static effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/12—Combinations of two or more pumps the pumps being of different types at least one pump being of the rotary-piston positive-displacement type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04B15/02—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being viscous or non-homogeneous
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04B15/04—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts the fluids being hot or corrosive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/08—Combinations of two or more pumps the pumps being of different types
- F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0023—Axial sealings for working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0096—Heating; Cooling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/084—Toothed wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/086—Carter
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
-
- 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
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P20/00—Technologies relating to chemical industry
- Y02P20/10—Process efficiency
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
The invention relates to the field of pumps, in particular to a melt pump for conveying high-temperature high-pressure high-viscosity media, wherein a driving gear shaft and a driven gear shaft which are meshed with each other are arranged in a working cavity of a pump body, the gear teeth of the driving gear shaft and the driven gear shaft are used for extruding the media through rotary meshing, a feeding pipe and a discharging pipe of the pump body are respectively communicated with corresponding boosting pipes, boosting plungers which can be respectively inserted into the feeding pipe and the discharging pipe to generate extrusion action on the media are respectively arranged in the two boosting pipes, and two driving ends of a reciprocating driving source are respectively connected with the corresponding boosting plungers, so that driving forces with opposite directions are provided for the two boosting plungers at the same time; and a heating system is arranged in the two gear shafts and/or on the outer ring of the pump body. The invention avoids the reduction of the viscosity of the medium with the help of the heating system, and greatly improves the conveying speed of the high-temperature high-pressure high-viscosity medium by being matched with the plunger.
Description
Technical Field
The invention relates to the field of pumps, in particular to a melt pump for conveying high-temperature high-pressure high-viscosity media.
Background
The melt pump is a positive displacement conveying device, the flow rate and the rotation speed of the pump are in strict proportional relation, and the main structure of the melt pump mainly comprises a pump shell, a driving gear shaft, a driven gear shaft, a bearing, front and rear end plates and a packing seal. The gear tooth profile of the two gear shafts, the pump body and the side cover plate are matched with each other to form a feeding area, a conveying area and a discharging area of the pump, and melt media are conveyed by means of working volume change caused by mutual meshing of the driving gear shaft and the driven gear shaft in operation. When the gear shaft rotates in a specified direction, the melt enters the tooth grooves of the gear shaft, and is brought into the material conveying area from two sides along with the rotation of the gear shaft, and the gears are meshed again, so that the melt in the tooth grooves is extruded.
Under the specific conveying working conditions of high temperature (more than 250 ℃), high pressure (more than 25 MPa) and high viscosity medium (more than 12000 Pas), the medium in the melt pump is easily influenced by external cold air, so that the temperature of the medium is reduced, the viscosity is improved, and the conveying speed is reduced; meanwhile, before entering the melt pump and after exiting the melt pump, the medium naturally flows in the pipeline by gravity, and as the heat insulation performance of the pipeline is inferior to that of the melt pump, the temperature of the medium is reduced due to the fact that the medium is more easily influenced by external cold air in the pipeline, the viscosity of the medium is further improved, and the conveying speed of the medium is reduced, so that the problem needs to be solved.
Disclosure of Invention
In order to avoid and overcome the technical problems in the prior art, the invention provides a melt pump for conveying high-temperature high-pressure high-viscosity media. The invention avoids the reduction of the viscosity of the medium with the help of the heating system, and greatly improves the conveying speed of the high-temperature high-pressure high-viscosity medium by being matched with the plunger.
In order to achieve the above purpose, the present invention provides the following technical solutions:
the melt pump comprises a pump body, a working cavity, a feeding pipe, a discharging pipe, a feeding pipe, a discharging pipe, a reciprocating driving source, a driving plunger, a driving gear shaft, a driven gear shaft, a feeding pipe and a discharging pipe, wherein the working cavity of the pump body is internally provided with the driving gear shaft and the driven gear shaft which are meshed with each other; and a heating system is arranged in the two gear shafts and/or on the outer ring of the pump body.
As a further scheme of the invention: the heating system comprises a sleeve arranged in the mounting cavity, the sleeve is in coaxial rotary fit with the corresponding gear shaft through a support bearing, and a heating medium is filled in the sleeve.
As still further aspects of the invention: the sleeve is a double-layer sleeve, the tube cavity of the sleeve comprises an inner cavity and an annular clamping cavity which is arranged around the inner cavity, the inner cavity and the clamping cavity are mutually communicated, a first heat medium inlet which is communicated with the clamping cavity and a first heat medium outlet which is communicated with the inner cavity are formed in the sleeve, and heat medium sequentially passes through the first heat medium inlet, the clamping cavity and the inner cavity and then is discharged from the first heat medium outlet, so that the circulating flow of the heat medium is realized.
As still further aspects of the invention: and a sealing piece which is in rotary fit with the sleeve is arranged at the opening of the installation cavity so as to prevent heat in the installation cavity from being dissipated.
As still further aspects of the invention: the heating system comprises a heat preservation jacket coaxially sleeved outside the pump body, an annular jacket cavity positioned on the outer ring of the working cavity is formed in the heat preservation jacket, a second heat medium inlet and a second heat medium outlet are formed in the heat preservation jacket, and heat medium enters the jacket cavity along the second heat medium inlet and then is discharged from the second heat medium outlet, so that circulating flow of the heat medium is realized.
As still further aspects of the invention: the end parts of the driving gear shaft and the driven gear shaft in the pump body are provided with shaft head seals, the shaft head seals comprise reverse spiral sleeves which are coaxially arranged with the corresponding gear shafts, the matching surfaces of the reverse spiral sleeves and the corresponding gear shafts are provided with thread grooves, and the rotation directions of the thread grooves are opposite to the rotation directions of the corresponding gear shafts.
As still further aspects of the invention: the shaft head seal also comprises graphite fillers which are coaxially arranged with the corresponding gear shafts, and the reverse spiral sleeve and the graphite fillers are sequentially arranged along the direction far away from the working cavity.
As still further aspects of the invention: the feeding pipe and the discharging pipe are respectively arranged at the top and the bottom of the pump body along the vertical direction, the reciprocating driving source is a reciprocating hydraulic pump or a reciprocating pneumatic pump, the reciprocating driving source is arranged along the vertical direction so as to generate reciprocating motion along the vertical direction, the two boosting pipes are arranged in parallel along the horizontal direction, one end of each boosting pipe is communicated with the feeding pipe or the discharging pipe, the other end of each boosting pipe is communicated with one driving end of the reciprocating driving source, the boosting plunger is driven by the reciprocating driving source so as to reciprocate in the pipe cavity of the boosting pipe, and the reciprocating motion track of the boosting plunger is intersected with the pipe cavity of the feeding pipe or the discharging pipe.
As still further aspects of the invention: the outer profile curve of the gear teeth comprises a first tooth root arc section, a first concave tooth profile section, a first parabolic section, a first convex tooth profile section, a tooth top arc section, a second convex tooth profile section, a second parabolic section, a second concave tooth profile section and a second tooth root arc section which are connected in sequence; the first tooth profile segment and the second tooth profile segment are symmetrically arranged about the top arc segment, the first parabolic segment and the second parabolic segment are symmetrically arranged about the top arc segment, the first tooth profile segment and the second tooth profile segment are symmetrically arranged about the top arc segment, and the first tooth root arc segment and the second tooth root arc segment are symmetrically arranged about the top arc segment;
after the pitch line of the gear teeth is processed and converted into a straight line, a rectangular coordinate system is established by taking the pitch line of the gear teeth as an X axis, and a Y axis of the rectangular coordinate system passes through the tooth root on the right side of the gear teeth;
the first tooth root arc section, the first concave tooth profile section, the first convex tooth profile section, the tooth top arc section, the second convex tooth profile section, the second concave tooth profile section and the second tooth root arc section are all arc lines; the first parabolic section and the second parabolic section are parabolic;
the ordinate of the arc section of the tooth top ish a The abscissa at the two end points of the addendum arc segment is:
wherein, the radius of the addendum circle of the addendum arc sectionR A5 =U+h a ；
UThe pitch circle radius of the gear teeth;
ρ a the radius of the arc is the radius of the tooth profile section of the second convex tooth;
h a is the tooth top of the gear teeth;
X a the circle center distance of the tooth profile section of the second convex tooth;
L a the circle center offset of the tooth profile section of the second convex tooth;
M n is the pitch of the gear teeth;
the circle center coordinates of the second convex tooth profile section are as follows:
；
the arc initial angle of the second convex tooth profile section is as follows:
；
the arc termination angle of the second convex tooth profile section is as follows:δ 1 ；
δ 1 meanwhile, the convex tooth process angle of the gear teeth is also formed;
the parabolic equation for the second parabolic segment is:Y=Kx 2 +b；
wherein ,Kis parabolic coefficient;
bis the distance from the vertex of the parabola to the pitch line;
the parabola of the second parabolic segment crosses the following two coordinate points:
wherein ,h ja a distance from the intersection point of the second parabolic section and the second convex tooth profile section to the pitch line;
L f the circle center offset of the tooth profile section of the second concave tooth;
h jf a distance from an intersection point of the second parabolic section and the second concave tooth profile section to the pitch line;
ρ f arc radius of the second concave tooth profile section;
δ 2 is a concave technological angle of the gear teeth;
the center coordinates of the tooth profile section of the second concave tooth areL f ，X f ）；
The arc initial angle of the second concave tooth profile section is as follows:
；
arc termination angle of second concave tooth profile section:
；
wherein ,h f the tooth root of the gear tooth is high;
X f the circle center distance of the tooth profile section of the second concave tooth is the circle center distance;
the circle center coordinates of the second tooth root arc section are as follows:
；
the arc starting angle of the second tooth root arc section is as follows:
；
arc termination angle of the second root arc segment:
。
compared with the prior art, the invention has the beneficial effects that:
1. according to the invention, two groups of boosting plungers are arranged at the feeding pipe and the discharging pipe of the pump body, and the speed of medium entering the pump body or being discharged out of the pump body is accelerated by boosting of the plungers; the two groups of boosting pipes are communicated with the two driving ends of the reciprocating driving source, and can drive the two groups of boosting plungers to boost in opposite motion states through one driving source at the same time, so that the driving efficiency is high; the medium is maintained at a preset temperature by the heating system while the plunger is assisted, so that the viscosity of the medium is prevented from being reduced, and the conveying speed of the high-temperature high-pressure high-viscosity medium is greatly improved.
2. According to the invention, the installation cavity is formed in the gear shaft so as to be used for installing the sleeve, and the heating medium enters the clamping cavity from the first heating medium inlet of the sleeve, is reversed through the inner cavity and is discharged from the first heating medium outlet, so that the circulating flow of the maximum flow path is realized; because the installation cavity is in a sealed state, the heating of the installation cavity is realized when the heating medium flows, heat is outwards dispersed from the installation cavity, the heating effect on the gear shaft is achieved, and the temperature of the medium is stable through shaft heating.
3. The heat-insulating jacket is arranged outside the pump body, and the heating medium is discharged from the second heating medium outlet after entering the jacket cavity from the second heating medium inlet, so that the circulating flow of the heating medium is realized, the heating medium is heated from outside to inside, the bidirectional heating can be realized under the cooperation of the shaft heating system, the medium temperature in the pump body is kept in a constant state all the time, and the heating efficiency is high.
4. The reverse spiral arrangement of the reverse spiral sleeve on the shaft head seal can prevent the medium in the pump body from leaking outwards, and after the reverse spiral sleeve is matched with graphite filler, the sealing performance of the shaft head can be ensured to be good, and the reverse spiral arrangement is suitable for the high-pressure working condition in the pump body.
5. The gear teeth on the gear shaft can generate specific meshing gaps when the driving gear shaft and the driven gear shaft are meshed by arranging the unique molded lines, so that the gear is more suitable for the working conditions of high temperature, high pressure and high viscosity, and the conveying efficiency of a medium is maximized.
Drawings
Fig. 1 is a schematic structural view of the present invention.
Fig. 2 is a schematic view of the internal structure of the pump body according to the present invention.
Fig. 3 is a top view of the pump body of the present invention.
Fig. 4 is a schematic view of the structure of the shaft head seal in the present invention.
Fig. 5 is a schematic view of the outer profile of the gear teeth of the present invention.
In the figure:
1. a pump body; 11. a feed pipe; 111. a feed inlet; 12. a discharge pipe; 121. a discharge port;
13. a drive gear shaft; 14. a driven gear shaft; 15. a shaft heating system;
151. a first heating medium inlet; 152. a first heating medium outlet; 153. a mounting cavity;
154. a sleeve; 1541. clamping a cavity; 1542. an inner cavity; 155. a support bearing;
16. a heat preservation jacket; 161. a second heating medium inlet; 162. a jacket cavity; 163. a second heating medium outlet;
17. sealing the shaft head; 171. a reverse spiral sleeve; 172. a graphite filler;
18. a working chamber; 19. gear teeth;
a1, a first tooth root arc section; a2, a first concave tooth profile section; a3, a first parabolic section;
a4, a first convex tooth profile section; a5, a tooth top arc section; a6, a second convex tooth profile section;
a7, a second parabolic section; a8, a second concave tooth profile section; a9, a second tooth root arc section;
2. a boosting pipe; 21. boosting the plunger; 3. a driving motor; 4. a reciprocating drive source.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Referring to fig. 1 to 5, in an embodiment of the present invention, a melt pump for conveying high-temperature, high-pressure and high-viscosity media includes a pump body 1, a driving gear shaft 13 and a driven gear shaft 14 are disposed in a working cavity 18 of the pump body 1, and the driving gear shaft 13 and the driven gear shaft 14 are rotationally matched with the pump body 1 through corresponding bearing structures. One end of the driving gear shaft 13 extends out of the pump body 1 and is coaxially fixed with a motor shaft of the driving motor 3, and the driving gear shaft 13 is arranged in meshing engagement with the driven gear shaft 14, so that the driving gear shaft 13 and the driven gear shaft 14 can be driven to rotate in opposite rotational directions when the driving motor 3 is operated. The driving gear shaft 13 and the driven gear shaft 14 are formed by integrally machining and forming shafts and gears.
The top of the pump body 1 is provided with a feeding pipe 11 along the vertical direction, the bottom of the pump body 1 is provided with a discharging pipe 12 along the vertical direction, and the feeding pipe 11 and the pipe body of the discharging pipe 12 are positioned on the same straight line. The pipe body at the top of the feeding pipe 11 is communicated with the boosting pipe 2 which is horizontally arranged after being bent by ninety degrees, the feeding hole 111 of the feeding pipe 11 is arranged on the pipe body at the horizontal section of the feeding pipe, and the opening of the feeding hole 111 is upward.
The bottom of the discharging pipe 12 is provided with a discharging hole 121 with a downward opening, the pipe body of the discharging pipe 12 is communicated with the other group of boosting pipes 2 which are horizontally arranged, and the joint height of the boosting pipes 2 and the discharging pipe 12 is positioned between the pump body 1 and the discharging hole 121.
The two booster pipes 2 are identical in construction, preferably arranged in a horizontal direction and parallel to each other. The boosting plungers 21 capable of reciprocating along the length direction of the pipe body are arranged in the pipe body of the boosting pipe 2, and the contact surfaces of the boosting plungers 21 and the pipe body of the boosting pipe 2 are arranged in a sealing way; the tube cavity of one end of the two boosting tubes 2 far away from the pump body 1 is communicated with a reciprocating driving source 4. The reciprocating driving source 4 may be a reciprocating hydraulic pump or a reciprocating pneumatic pump, and the pressure in the tube cavity of the booster tube 2 is changed by injecting air, liquid or a piston into the tube cavity of the booster tube 2, so as to drive the booster plungers 21 in the two groups of booster tubes 2 to move.
The reciprocating driving source 4 is arranged along the vertical direction, and the two driving ends of the reciprocating driving source respectively drive the boosting plungers 21 in the two groups of boosting pipes 2 to move so that the movement states of the two groups of boosting plungers 21 are opposite, namely: when one group of the boosting plungers 21 is inserted into the horizontal section of the feeding pipe 11, the other group of the boosting plungers 21 is withdrawn from the discharging pipe 12; one set of boost plungers 21 is inserted into the tapping pipe 12 as the other set of boost plungers 21 is withdrawn from the horizontal section of the feed pipe 11. In the process that the two groups of boosting plungers 21 reciprocally enter the feeding pipe 11 and the discharging pipe 12, the medium in the pipe body is extruded, so that the medium entering the pump body 1 is quickened or the medium discharging is quickened.
In order to improve the tightness of the driving gear shaft 13 and the driven gear shaft 14, at least four sets of shaft head seals 17 are arranged in the pump body 1 and are respectively arranged at two ends of the shaft bodies of the driving gear shaft 13 and the driven gear shaft 14. The stub shaft seal 17 includes a counter-spiral sleeve 171 and graphite packing 172 coaxially with the corresponding gear shaft and disposed in sequence in a direction away from the working chamber 18, the counter-spiral sleeve 171 and graphite packing 172 preferably being compressed by a compression ring.
A screw groove is formed at the inner side of the reverse screw sleeve 171, and the rotation direction of the screw groove is opposite to the rotation direction of the corresponding gear shaft. In order to further improve the sealing effect, sealing rings are arranged on the contact surface of the pump body 1 and the reverse spiral sleeve 171, the contact surface of the compression ring and the pump body 1 and the contact surface of the compression ring and the reverse spiral sleeve 171.
In order to avoid that the medium temperature is lower than the set temperature, a shaft heating system 15 and a heat preservation jacket 16 are respectively arranged inside the pump body 1 and outside the pump body 1.
For installing the shaft heating system 15, the driving gear shaft 13 and the driven gear shaft 14 are internally provided with an installation cavity 153 along the axial direction, and one end of the installation cavity 153 away from the driving motor 3 is opened so as to avoid the position of the driving motor 3. The shaft heating system 15 includes a sleeve 154 axially insertable into the mounting cavity 153 along the mounting cavity 153, with at least two sets of support bearings 155 mounted within the mounting cavity 153 for rotational engagement with the sleeve 154 by the support bearings 155. In operation, the sleeve 154 is stationary and the corresponding gear shaft rotates.
The casing 154 has an inner and outer cavity within the body, the two cavities being separated by an annular plate. The lumen of the sleeve 154 includes a cylindrical inner lumen 1542 and an annular clip lumen 1541 disposed about the inner lumen 1542. The first heat medium inlet 151 and the first heat medium outlet 152 are installed at the ends of the sleeve 154 outside the installation cavity 153, and the first heat medium inlet 151 and the first heat medium outlet 152 are respectively communicated with the clamping cavity 1541 and the inner cavity 1542. The clip chamber 1541 and the end of the inner chamber 1542 away from the first heat medium inlet 151 and the first heat medium outlet 152 are in communication. The heating medium enters the nip chamber 1541 from the first heating medium inlet 151, is diverted through the inner chamber 1542 and exits the first heating medium outlet 152 to achieve a circular flow of maximum flow path.
To seal the interior of the mounting cavity 153 from heat dissipation, a seal is installed at the opening of the mounting cavity 153 to fill the gap between the sleeve 154 and the opening of the mounting cavity 153.
The shaft heating system 15 has an inside-out heating effect to stabilize the medium temperature. In order to further improve the heating effect, the outer ring of the pump body 1 is also fixed with a heat-insulating jacket 16, and a jacket cavity 162 surrounding the working cavity 18 is arranged in the heat-insulating jacket 16, or the heat-insulating jacket 16 and the outer wall of the pump body 1 are enclosed to form the jacket cavity 162. The heat preservation jacket 16 is provided with a second heat medium inlet 161 and a second heat medium outlet 163, and the positions of the second heat medium inlet 161 and the second heat medium outlet 163 are oppositely arranged. The heat medium enters the jacket cavity 162 from the second heat medium inlet 161 and is discharged from the second heat medium outlet 163, so that the circulation flow of the heat medium is realized, and the heat medium is heated from outside to inside.
The driving gear shaft 13 and the driven gear shaft 14 are made of high-grade nitriding steel 38CrMoAl materials, and have the characteristics of high wear resistance, high fatigue strength, high temperature resistance and the like. In order to make the inlet pressure of the pump body 1 lower and even be negative pressure, so the inlet caliber of the pump body 1 is enlarged, a large amount of medium can enter the working cavity 18 more freely and smoothly through the dead weight effect by the design of large caliber, and an upper-inlet and lower-outlet conveying mode is adopted. The front pump cover and the rear pump cover of the pump body 1 are made of high-strength martensitic stainless steel 1Cr13 materials, can bear higher stress, have good static and dynamic fracture toughness, high strength and hardness and better weldability. The sliding bearings used for the driving gear shaft 13 and the driven gear shaft 14 are made of high-carbon high-chromium tool steel SKD11, and are wear-resistant, corrosion-resistant and high-temperature-resistant.
The gears on the driving gear shaft 13 and the driven gear shaft 14 are provided with gear teeth 19 with the same size, the tooth roots of two adjacent groups of gear teeth 19 are used as starting points and end points, and the outer profile curve of the gear teeth 19 comprises a first tooth root circular arc section A1, a first concave tooth profile section A2, a first parabolic section A3, a first convex tooth profile section A4, a tooth top circular arc section A5, a second convex tooth profile section A6, a second parabolic section A7, a second concave tooth profile section A8 and a second tooth root circular arc section A9 which are connected in sequence.
The first tooth root arc section A1, the first concave tooth profile section A2, the first convex tooth profile section A4, the tooth top arc section A5, the second convex tooth profile section A6, the second concave tooth profile section A8 and the second tooth root arc section A9 are all arc lines; the first parabolic section A3 and the second parabolic section A7 are parabolic.
The first tooth profile segment A4 and the second tooth profile segment A6 are arranged in a bilateral symmetry manner with respect to the addendum arc segment A5, the first parabolic segment A3 and the second parabolic segment A7 are arranged in a bilateral symmetry manner with respect to the addendum arc segment A5, the first concave tooth profile segment A2 and the second concave tooth profile segment A8 are arranged in a bilateral symmetry manner with respect to the addendum arc segment A5, and the first root arc segment A1 and the second root arc segment A9 are arranged in a bilateral symmetry manner with respect to the addendum arc segment A5. Since the addendum arc segment A5 is a circular arc line with central symmetry, the bilateral symmetry refers to bilateral symmetry with the center line of the addendum arc segment A5 as the symmetry axis.
Establishing a rectangular coordinate system by taking a pitch line of the gear teeth 19 as an X axis, wherein a Y axis of the rectangular coordinate system passes through the tooth root of the gear teeth 19 and also passes through the axis of the gear shaft, and the Y axis coincides with the radius line of the tooth root; the tooth root on the right side represents the tooth root in front of the gear teeth 19 with the rotation direction of the gear teeth 19 as the front. It should be noted that the pitch line of the tooth 19 is actually a circle, and fig. 5 is for convenience of observation, the pitch line is converted into a straight line to form a rectangular coordinate system for convenience of observation, in which the ordinate of the addendum arc segment A5 ish a The abscissa at the two end points of the addendum arc segment A5 is:
wherein, the radius of the addendum circle of the addendum arc segment A5R A5 =U+h a ；
UA pitch radius for the gear teeth 19;
ρ a the radius of the arc of the tooth profile section A6 of the second convex tooth;
h a is the tooth top of the gear teeth 19;
X a for the second lobe profile segment A6The distance between circle centers is moved;
L a the circle center offset of the second convex tooth profile section A6;
M n is the pitch of the teeth 19;
the circle center coordinates of the second convex tooth profile section A6 are as follows:
；
the arc initial angle of the second convex tooth profile section A6 is as follows:
；
the arc termination angle of the second convex tooth profile section A6 is as follows:δ 1 ；
δ 1 and is also the tooth process angle of the tooth 19;
the parabolic equation for the second parabolic segment A7 is:Y=Kx 2 +b；
wherein ,Kis parabolic coefficient;
bis the distance from the vertex of the parabola to the pitch line;
the parabola of the second parabolic segment A7 crosses the following two coordinate points:
wherein ,h ja is the distance from the intersection point of the second parabolic section A7 and the second convex tooth profile section A6 to the pitch line;
L f the circle center offset of the second concave tooth profile section A8;
h jf distance from node line to intersection point of second parabolic section A7 and second concave tooth profile section A8Separating;
ρ f the arc radius of the second concave tooth profile section A8;
δ 2 a concave tooth process angle for the gear teeth 19;
the center coordinates of the second concave tooth profile section A8 are%L f ，X f ）；
The arc initial angle of the second concave tooth profile section A8 is as follows:
；
arc termination angle of second concave tooth profile segment A8:
；
wherein ,h f the tooth root height for tooth 19;
X f the circle center distance of the second concave tooth profile section A8;
the circle center coordinates of the second tooth root arc section A9 are as follows:
；
the arc starting angle of the second tooth root arc section A9 is as follows:
；
arc termination angle of the second root arc segment A9:
。
the pressure angle α of the teeth 19 is preferably 24 °.
The first tooth root circular arc section A1, the first concave tooth profile section A2, the first parabolic section A3 and the first convex tooth profile section A4 are respectively and symmetrically arranged with the second convex tooth profile section A6, the second parabolic section A7, the second concave tooth profile section A8 and the second tooth root circular arc section A9, so that after the curves of the second convex tooth profile section A6, the second parabolic section A7, the second concave tooth profile section A8 and the second tooth root circular arc section A9 are obtained, the curves of the first tooth root circular arc section A1, the first concave tooth profile section A2, the first parabolic section A3 and the first convex tooth profile section A4 can be correspondingly obtained.
The following table shows the modulus at different normalGPreferred values for each parameter of the lower cog 19.
The following table shows the performance comparison between the melt pump of the present invention and the existing YCB external engagement melt pump, and it can be seen that, at the same rotation speed, the end face clearance of the melt pump of the present invention is lower than that of the existing YCB external engagement melt pump, and the volumetric efficiency of the pump is higher than that of the existing YCB external engagement melt pump, and the performance is greatly improved.
The basic principles of the present application have been described above in connection with specific embodiments, however, it should be noted that the advantages, benefits, effects, etc. mentioned in the present application are merely examples and not limiting, and these advantages, benefits, effects, etc. are not to be considered as necessarily possessed by the various embodiments of the present application. Furthermore, the specific details disclosed herein are for purposes of illustration and understanding only, and are not intended to be limiting, as the application is not intended to be limited to the details disclosed herein as such.
The block diagrams of the devices, apparatuses, devices, systems referred to in this application are only illustrative examples and are not intended to require or imply that the connections, arrangements, configurations must be made in the manner shown in the block diagrams. As will be appreciated by one of skill in the art, the devices, apparatuses, devices, systems may be connected, arranged, configured in any manner. Words such as "including," "comprising," "having," and the like are words of openness and mean "including but not limited to," and are used interchangeably therewith. The terms "or" and "as used herein refer to and are used interchangeably with the term" and/or "unless the context clearly indicates otherwise. The term "such as" as used herein refers to, and is used interchangeably with, the phrase "such as, but not limited to.
It is also noted that in the apparatus, devices and methods of the present application, the components or steps may be disassembled and/or assembled. Such decomposition and/or recombination should be considered as equivalent to the present application.
The previous description of the disclosed aspects is provided to enable any person skilled in the art to make or use the present application. Various modifications to these aspects will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other aspects without departing from the scope of the application. Thus, the present application is not intended to be limited to the aspects shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
The foregoing description has been presented for purposes of illustration and description. Furthermore, this description is not intended to limit the embodiments of the application to the form disclosed herein. Although a number of example aspects and embodiments have been discussed above, a person of ordinary skill in the art will recognize certain variations, modifications, alterations, additions, and subcombinations thereof.
Claims (9)
1. A melt pump for conveying high-temperature high-pressure high-viscosity medium, wherein a driving gear shaft (13) and a driven gear shaft (14) which are meshed with each other are arranged in a working cavity (18) of a pump body (1), gear teeth (19) of the driving gear shaft (13) and the driven gear shaft (14) extrude the medium through rotary meshing, and the melt pump is characterized in that a feeding pipe (11) and a discharging pipe (12) of the pump body (1) are respectively communicated with a group of boosting pipes (2), boosting plungers (21) which can be respectively inserted into the feeding pipe (11) and the discharging pipe (12) to generate a squeezing action on the medium are respectively arranged in the two boosting pipes (2), and two driving ends of a reciprocating driving source (4) are respectively connected with the two groups of boosting plungers (21), so that driving forces with opposite directions are provided for the two boosting plungers (21) at the same time; and a heating system is arranged in the two gear shafts and/or on the outer ring of the pump body (1).
2. The melt pump for conveying high-temperature, high-pressure and high-viscosity media according to claim 1, wherein the driving gear shaft (13) and the driven gear shaft (14) are internally provided with a mounting cavity (153) along the axial direction, the heating system comprises a sleeve (154) arranged in the mounting cavity (153), the sleeve (154) is coaxially and rotatably matched with the corresponding gear shaft through a supporting bearing (155), and the sleeve (154) is filled with heating media.
3. The melt pump for conveying high-temperature, high-pressure and high-viscosity media according to claim 2, wherein the sleeve (154) is a double-layer sleeve, the lumen of the sleeve (154) comprises an inner cavity (1542) and an annular clamping cavity (1541) arranged around the inner cavity (1542), the inner cavity (1542) and the clamping cavity (1541) are communicated with each other, the sleeve (154) is provided with a first heat medium inlet (151) communicated with the clamping cavity (1541) and a first heat medium outlet (152) communicated with the inner cavity (1542), and heat medium sequentially passes through the first heat medium inlet (151), the clamping cavity (1541) and the inner cavity (1542) and then is discharged from the first heat medium outlet (152) so as to realize circulation flow of the heat medium.
4. A melt pump for transporting high temperature, high pressure and high viscosity media according to claim 2, wherein said mounting cavity (153) is open at one side for the insertion of the sleeve (154), and a seal member in rotary fit with the sleeve (154) is arranged at the opening of the mounting cavity (153) to prevent heat dissipation in the mounting cavity (153).
5. The melt pump for delivering high-temperature, high-pressure and high-viscosity medium according to any one of claims 1 to 4, wherein the heating system comprises a heat preservation jacket (16) coaxially sleeved outside the pump body (1), an annular jacket cavity (162) positioned at the outer ring of the working cavity (18) is formed in the heat preservation jacket (16), a second heat medium inlet (161) and a second heat medium outlet (163) are formed in the heat preservation jacket (16), and the heat medium is discharged from the second heat medium outlet (163) after entering the jacket cavity (162) along the second heat medium inlet (161) so as to realize the circulation flow of the heat medium.
6. The melt pump for conveying high-temperature, high-pressure and high-viscosity media according to any one of claims 1 to 4, wherein a shaft head seal (17) is arranged at the end parts of a driving gear shaft (13) and a driven gear shaft (14) in the pump body (1), the shaft head seal (17) comprises a reverse spiral sleeve (171) coaxially arranged with a corresponding gear shaft, a thread groove is formed in a matching surface of the reverse spiral sleeve (171) and the corresponding gear shaft, and the rotation direction of the thread groove is opposite to the rotation direction of the corresponding gear shaft.
7. A melt pump for transporting high temperature, high pressure, high viscosity media as defined in claim 6 wherein said shaft head seal (17) further comprises graphite packing (172) coaxially disposed with the corresponding gear shaft, the counter-spiral sleeve (171) and graphite packing (172) being disposed in sequence in a direction away from the working chamber (18).
8. Melt pump for conveying high-temperature, high-pressure and high-viscosity media according to any one of claims 1 to 4, characterized in that the feed pipe (11) and the discharge pipe (12) are respectively arranged at the top and the bottom of the pump body (1) along the vertical direction, the reciprocating driving source (4) is a reciprocating hydraulic pump or a reciprocating pneumatic pump, the reciprocating driving source (4) is arranged along the vertical direction so as to generate a reciprocating motion along the vertical direction, the two boosting pipes (2) are arranged in parallel with each other along the horizontal direction, one end of the boosting pipes (2) is communicated with the feed pipe (11) or the discharge pipe (12), the other end of the boosting pipe (2) is communicated with one driving end of the reciprocating driving source (4), the boosting plunger (21) is driven by the reciprocating driving source (4) so as to reciprocate in the pipe cavity of the boosting pipe (2), and the reciprocating motion track of the boosting plunger (21) intersects with the pipe cavity of the feed pipe (11) or the discharge pipe (12).
9. The melt pump for conveying high-temperature, high-pressure and high-viscosity media according to any one of claims 1 to 4, wherein the driving gear shaft (13) and the driven gear shaft (14) have the same gear teeth (19), and the outer profile curve of the gear teeth (19) comprises a first tooth root arc section (A1), a first concave tooth profile section (A2), a first parabolic section (A3), a first convex tooth profile section (A4), a top arc section (A5), a second convex tooth profile section (A6), a second parabolic section (A7), a second concave tooth profile section (A8) and a second tooth root arc section (A9) which are sequentially connected; the first convex tooth profile section (A4) and the second convex tooth profile section (A6) are symmetrically arranged about the top arc section (A5), the first parabolic section (A3) and the second parabolic section (A7) are symmetrically arranged about the top arc section (A5), the first concave tooth profile section (A2) and the second concave tooth profile section (A8) are symmetrically arranged about the top arc section (A5), and the first root arc section (A1) and the second root arc section (A9) are symmetrically arranged about the top arc section (A5);
after the pitch line of the gear teeth (19) is processed and converted into a straight line, a rectangular coordinate system is established by taking the pitch line of the gear teeth (19) as an X axis, and a Y axis of the rectangular coordinate system passes through the tooth root on the right side of the gear teeth (19);
the first tooth root arc section (A1), the first concave tooth profile section (A2), the first convex tooth profile section (A4), the tooth top arc section (A5), the second convex tooth profile section (A6), the second concave tooth profile section (A8) and the second tooth root arc section (A9) are all arc lines; the first parabolic section (A3) and the second parabolic section (A7) are parabolic;
the ordinate of the tooth top arc section (A5) ish a The abscissa at the two end points of the addendum arc segment (A5) is:
UIs the pitch radius of the gear teeth (19);
ρ a is the arc radius of the second convex tooth profile section (A6);
h a is the tooth top of the gear teeth (19);
X a the circle center distance of the second convex tooth profile section (A6);
L a is the circle center offset of the second convex tooth profile section (A6);
M n is the pitch of the gear teeth (19);
the circle center coordinates of the second convex tooth profile section (A6) are as follows:
the method comprises the steps of carrying out a first treatment on the surface of the The arc starting angle of the second convex tooth profile section (A6) is as follows: />
The method comprises the steps of carrying out a first treatment on the surface of the The arc termination angle of the second convex tooth profile section (A6) is as follows:δ 1 ；
δ 1 simultaneously, the convex tooth process angle of the gear teeth (19);
the parabolic equation for the second parabolic section (A7) is:Y=Kx 2 +b；
wherein ,Kis parabolic coefficient;
bis the distance from the vertex of the parabola to the pitch line;
the parabola of the second parabolic section (A7) crosses the following two coordinate points:
L f is the circle center offset of the second concave tooth profile section (A8);
h jf is the distance from the intersection point of the second parabolic section (A7) and the second concave tooth profile section (A8) to the pitch line;
ρ f is the arc radius of the second concave tooth profile section (A8);
δ 2 is a concave tooth process angle of the gear teeth (19);
the center coordinates of the second concave tooth profile section (A8) are%L f ，X f ）；
The arc initial angle of the second concave tooth profile section (A8) is as follows:
the method comprises the steps of carrying out a first treatment on the surface of the Arc termination angle of second concave tooth profile segment (A8):
； wherein ,h f is the tooth root height of the gear teeth (19);
X f the circle center distance of the second concave tooth profile section (A8) is measured;
the center coordinates of the second tooth root arc section (A9) are as follows:
the method comprises the steps of carrying out a first treatment on the surface of the The arc starting angle of the second tooth root arc section (A9) is as follows:
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| CN202310498576.4A CN116221058B (en) | 2023-05-06 | 2023-05-06 | Melt pump for conveying high-temperature high-pressure high-viscosity medium |
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