CN102619779B - Turbulence generator for medium-consistency paper pulp pump - Google Patents
Turbulence generator for medium-consistency paper pulp pump Download PDFInfo
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- CN102619779B CN102619779B CN201210095659.0A CN201210095659A CN102619779B CN 102619779 B CN102619779 B CN 102619779B CN 201210095659 A CN201210095659 A CN 201210095659A CN 102619779 B CN102619779 B CN 102619779B
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Abstract
The invention relates to a turbulence generator, in particular to a turbulence generator for a medium-consistency paper pulp pump. The turbulence generator is mounted at the front end of a pump impeller; the turbulence generator and the pump impeller are arranged on the same shaft; and the turbulence generator consists of a hub and a spiral blade fixed on the hub. The turbulence generator is characterized in that the spiral blade consists of an inlet surface, a work surface, a back surface, an outlet surface and an outer edge surface; the work surface is a three-dimensional space curved surface and consists of an inlet side, a blade edge section line and an outlet side; the back surface is formed by thickening the work surface at equal thickness; the inlet side is perpendicular to the axial direction; the outlet side is also perpendicular to the axial direction; and the inlet side and the outlet side rotate for an angle in the circumferential direction to form a blade wrap angle. According to the turbulence generator disclosed by the invention, the fluidizing and gas separating functions of medium-consistency paper pulp suspension can be realized and the conveying difficult problem caused by lack of flowability and over-high gas holdup of medium-consistency paper pulp is solved.
Description
Technical field
The present invention relates to a kind of turbulent flow generator, refer in particular to a kind of turbulent flow generator being applicable to medium concentration pulp pump.
Background technique
In dense conveying technology refer in pulping and papermaking processes, particularly in course of conveying, paper pulp is directly with the technology that middle concentration (pulp quality concentration 7%-15%) is carried; Compared to the conveying of conventional low density paper pulp, considerably reduce the water consumption in pulping process and paper waste discharge amount, greatly reduce the pollution to environment.
During pulp quality concentration C >=7%, paper pulp loses self mobility, and now slurry pulp is interior containing a large amount of gas simultaneously, and Low-consistency Stock Pump cannot be carried; Centrifugal middle underflow pump, compared with common low-consistency, adds turbulent flow generator.Turbulent flow generator is the critical component of medium concentration pulp pump, is arranged on middle underflow pump import position; By turbulent flow generator, Medium-Consistency Suspension achieves fluidization and gas-liquid separation, then produces flow and lift by other hydraulic part of pump, achieves the smooth delivery of power of middle concentration paper pulp; Therefore, turbulent flow generator is that can Medium-Consistency Suspension the prerequisite of smooth delivery of power, and the performance of turbulent flow generator directly determines conveying effect and the transfer efficiency of medium concentration pulp pump.
Chinese patent CN1851118A discloses high consistency pulp fluidization device in one, primarily of the blade composition be fixed on wheel hub, the scope at leaf curling angle is 10 ° ~ 75 °, blade rotation direction is contrary with impeller rotation direction, and vane nose gos deep in slurry standpipe, and root of blade is fixed on wheel hub, the scope that this patent just gives leaf curling angle is 10 ° ~ 75 °, do not relate to concrete angle how value, and angular range is too large, specific design cannot be determined.
Chinese patent CN201598531U discloses a kind of impeller becoming helix angle turbulent flow generator formula, describe the shape of impeller, point out that wherein turbulent flow generating mechanism comprises the stiffening ring between helical convex tendon and convex tendon becoming helix angle simultaneously, convex tendon one end is connected with impeller blade, and the scope of helix angle is for being 24 ° ~ 82 °; But this patent does not relate to concrete helix angle obtaining value method, does not relate to the design method of other size, turbulent flow generator can not be designed according to this description.
Through retrieval, also there is no the design method of turbulence generator for medium-consistency paper pulp pump vane type line at present, have impact on the research and development of medium concentration pulp pump and further apply.Therefore, the design method of research turbulence generator for medium-consistency paper pulp pump vane type line, can promote the raising of middle concentration paper pulp pump performance, the application and development of dense conveying technology in promotion.
Summary of the invention
The object of the invention is to the shortcoming overcoming prior art, provide a kind of can realize above-mentioned in the design method of turbulence generator for medium-consistency paper pulp pump vane type line of dense conveying technology; By this design method, can turbulent flow generator be designed, realize the effect of Medium-Consistency Suspension fluidization and divided gas flow, solve middle concentration paper pulp for want of self mobility and gas holdup excessive cause a conveying difficult problem.
The technical solution adopted for the present invention to solve the technical problems is: a kind of turbulence generator for medium-consistency paper pulp pump, described turbulent flow generator is installed on pump impeller front end, be installed on same axle with pump impeller, turbulent flow generator is made up of wheel hub and the spiral vane be fixed on wheel hub, it is characterized in that: spiral vane is made up of inlet face, working surface, the back side, exit face and outer edge surface; Wherein working surface is three-dimensional space curved surface, is made up of inlet side, blade outer rim molded line (vane type line) and Exit-edge, and the back side is thickeied by working surface equal thickness and forms; Inlet side is perpendicular to axial direction, and Exit-edge is also perpendicular to axial direction, but inlet side, Exit-edge turn over an angle formation subtended angle of blade in a circumferential direction.
Described a kind of turbulence generator for medium-consistency paper pulp pump, is characterized in that: described inlet face and the radius of exit face are all the half of spiral vane thickness.
Described a kind of turbulence generator for medium-consistency paper pulp pump, is characterized in that: described spiral vane launches along the axial direction of wheel hub, vertical with wheel hub; Spiral vane and wheel hub joint are with the arc transition of radius 10 ~ 40mm.
Described a kind of turbulence generator for medium-consistency paper pulp pump, is characterized in that: the spiral vane number of described turbulent flow generator gets the half of pump impeller blade number, generally gets 3 or 4.
Described a kind of turbulence generator for medium-consistency paper pulp pump, is characterized in that: the spiral vane outside diameter d of described turbulent flow generator
2get pump impeller blade inlet diameter, axial overall length
lrelevant to paper pulp flow velocity, determine its span by formula (1).The helix molded line that described blade outer rim molded line adopts variable pitch to combine with uniform pitch, to produce certain shearing stress, ensures certain gas deliverability simultaneously.Inlet part adopts uniform pitch molded line, and exit portion adopts variable pitch molded line; The length of the medium pitch section of blade axial overall length
sdetermined by formula (2), in blade axial overall length, the length of variable pitch section is
l 1,
.
（1）
（2）
Wherein,
Wherein:
qfor pump volume flow (m
3/ h);
for Media density (kg/m
3);
nfor turbulent flow generator rotating speed (r/min);
for turbulent flow generator angular velocity of rotation (rad/s), by
determine; d
2for turbulent flow generator outer blade diameter (m);
d h for turbulent flow generator hub diameter (m), get (0.2 ~ 0.4) d
2; v
mfor media flow axial velocity (m/s);
afor the long-pending (m of turbulent flow generator cross section of fluid channel
2);
zfor the turbulent flow generator number of blade,
δfor vane thickness (m) equals the vane thickness of pump impeller;
sfor the length (m) of the medium pitch section of blade axial overall length;
for uniform pitch section cornerite;
βfor the inlet angle of blade outer rim molded line starting point.
Described turbulent flow generator blade outer rim molded line is on the same cylndrical surface of line centered by hub axis, and the arbitrfary point on blade outer rim molded line often turns over angle relative to the outlet of blade outer rim molded line at circumferencial direction
time, the length that corresponding circumferencial direction launches is
y, the length that axial direction launches is
x, the length that the axial direction of corresponding variable pitch section launches is
x ', the length that the axial direction of uniform pitch section launches is
x ' ', and
x=x '+x ' '.
Described vane type line blade angle a (x) adopts piecewise function to represent, outlet variable pitch molded line blade angle is determined by formula (3), and import uniform pitch molded line blade angle is determined by formula (4).
（3）
（4）
Wherein:
α(
x) be blade outer rim molded line blade angle, it to be specially on blade outer rim molded line arbitrfary point tangent direction and by the angle between this circumferencial direction,
α 0for the exit angle of blade outer rim molded line terminal, it is specially the angle between blade outer rim molded line exit tangent direction and circumferencial direction.
βfor the inlet angle of blade outer rim molded line starting point, it is specially the angle between blade outer rim molded line import tangent direction and circumferencial direction.
Described exit angle
α 0value is generally 85o – 90o, and namely blade outer rim molded line Way out almost extends in the axial direction; The inlet angle of blade outer rim molded line starting point
βgenerally get 25 °.
The length that circumferencial direction launches
ydetermined by formula (5):
（5）
For any point in blade outer rim molded line unfolded drawing, corresponding angle has:
（6）
Formula (3) is substituted into formula (6), obtains variable pitch section circumferencial direction length of run
yanother representation:
（7）
Formula (7) is substituted into formula (5), obtains circumferencial direction and often turn over angle
the length of the axial direction expansion of time-varying pitch section
x 'value:
（8）
In like manner, formula (4) is substituted into formula (6), then substitutes into formula (5), obtain circumferencial direction and often turn over angle
time uniform pitch section the length launched of axial direction
x ' 'value:
（9）
Wherein
for the angle that inlet side and Exit-edge turn in a circumferential direction, i.e. subtended angle of blade, value is 90o-120o,
for uniform pitch section cornerite, get (1/4-1/3)
.
The present invention compared to existing technology, has the following advantages:
1. can produce enough shearing stresses, make medium consistency fluidization;
2. can produce higher lift, improve gas deliverability;
3. be connected smooth with the impeller be arranged on below, reduce hydraulic loss.
Accompanying drawing explanation
Fig. 1 is middle underflow pump impeller assembly schematic three dimensional views, wherein 1. pump impeller, 2. turbulent flow generator;
Fig. 2 is turbulence generator for medium-consistency paper pulp pump structural representation, wherein: 3. turbulent flow generator wheel hub, 4. turbulent flow generator spiral vane, 5. inlet face, 6. working surface, the 7. back side, 8. exit face, 9. outer edge surface, 10. inlet side, 11. blade outer rim molded line, 12. Exit-edges; 13. spiral vanes and wheel hub joint;
Fig. 3 turbulence generator for medium-consistency paper pulp pump entrance edge of blade and Exit-edge direction schematic diagram.
Fig. 4 is turbulence generator for medium-consistency paper pulp pump physical dimension schematic diagram.
Fig. 5 is turbulence generator for medium-consistency paper pulp pump blade outer rim molded line schematic diagram.
Fig. 6 is turbulence generator for medium-consistency paper pulp pump blade outer rim molded line unfolded drawing.
Fig. 7 is turbulence generator for medium-consistency paper pulp pump surface vapor cloud charts.
Embodiment
Elaborate to enforcement of the present invention below, the present embodiment is implemented under premised on technical solution of the present invention, give detailed mode of execution and concrete operating process, but protection scope of the present invention is not limited to following embodiment.
As shown in Figure 1, the turbulent flow generator 1 of the present embodiment is installed on pump impeller 2 front end, is installed on same axle with pump impeller; As shown in Figure 2, turbulent flow generator is made up of wheel hub 3 and the spiral vane 4 be fixed on wheel hub.Spiral vane 4 is made up of inlet face 5, working surface 6, the back side 7, exit face 8 and outer edge surface 9.Wherein working surface 6 is three-dimensional space curved surface, is made up of inlet side 10, blade outer rim molded line (vane type line) 11 and Exit-edge 12, and the back side 7 is thickeied by working surface 6 equal thickness and forms.As shown in Figure 3, inlet side 10 is perpendicular to axial direction, and Exit-edge 12 is also perpendicular to axial direction, but inlet side 10, Exit-edge 12 turn over an angle in a circumferential direction, i.e. subtended angle of blade.
As shown in Figure 4, the turbulent flow generator outer blade diameter d of the present embodiment
2get pump impeller blade inlet diameter, axial overall length L is relevant to paper pulp flow velocity, determines its span by formula (1); The helix molded line that blade outer rim molded line adopts variable pitch to combine with uniform pitch, to produce certain shearing stress, ensures certain gas deliverability simultaneously.Inlet part adopts uniform pitch molded line, and exit portion adopts variable pitch molded line.The length of the medium pitch section of blade axial overall length
sdetermined by formula (2), in blade axial overall length, the length of variable pitch section is
l 1,
.
（1）
（2）
Wherein,
Wherein:
qfor pump volume flow (m
3/ h);
for Media density (kg/m
3);
nfor turbulent flow generator rotating speed (r/min);
for turbulent flow generator angular velocity of rotation (rad/s), by
determine; d
2for turbulent flow generator outer blade diameter (m);
d h for turbulent flow generator hub diameter (m), get (0.2 ~ 0.4) d
2; v
mfor media flow axial velocity (m/s);
afor the long-pending (m of turbulent flow generator cross section of fluid channel
2);
zfor the turbulent flow generator number of blade,
δfor vane thickness (m);
sfor uniform pitch section axial length (m);
for uniform pitch section cornerite.
Turbulent flow generator blade outer rim molded line is on the same cylndrical surface of line centered by hub axis, and the arbitrfary point on blade outer rim molded line often turns over angle relative to the outlet of blade outer rim molded line at circumferencial direction
time, the length that corresponding circumferencial direction launches is
y, the length that axial direction launches is
x, the length that the axial direction of corresponding variable pitch section launches is
x ', the length that the axial direction of uniform pitch section launches is
x ' ', and
x=x '+x ' ';
Blade outer rim molded line blade angle a (x) of the present embodiment adopts piecewise function to represent, variable pitch molded line blade angle is determined by formula (3), and uniform pitch molded line blade angle is determined by formula (4).
（3）
（4）
Wherein:
α(
x) be blade outer rim molded line blade angle, it to be specially on blade outer rim molded line arbitrfary point tangent direction and by the angle between this circumferencial direction,
α 0for the exit angle of blade outer rim molded line terminal, it is specially the angle between blade outer rim molded line exit tangent direction and circumferencial direction,
α 0value is generally 85o – 90o;
βfor the inlet angle of blade outer rim molded line starting point, it is specially the angle between blade outer rim molded line import tangent direction and circumferencial direction, inlet angle
βgenerally get 25 °.
On described turbulent flow generator blade outer rim molded line, arbitrfary point often turns over angle in a circumferential direction relative to the outlet of outer rim molded line
, circumferencial direction length of run corresponding in Fig. 6
ydetermined by formula (5), the length of the axial direction expansion of corresponding variable pitch section
x 'with the length that the axial direction of uniform pitch section launches
x ' 'determined by formula (8) and formula (9).
（5）
（8）
（9）
Wherein
for at axial distance
xthe angle circumferentially turned over that place is corresponding.
for uniform pitch section cornerite, get (1/4-1/3)
,
for subtended angle of blade, value is 90o-120o.
In the present embodiment, turbulent flow generator spiral vane 4 in axial direction launches, vertical with wheel hub 5, joint 13 with the arc transition of radius 30mm, vane thickness
be 12 mm.The number of blade gets the half of pump impeller blade number, and in the present embodiment, the turbulent flow generator number of blade is 4.
In the present embodiment, pump volume flow
qfor 600(m
3/ h), Media density
for 1250(kg/m
3), rotating speed
nbe 1450 (r/min), turbulent flow generator spiral vane 4 outside diameter d
2for 260mm, turbulent flow generator wheel hub 3 diameter is 95 mm.
In the present embodiment, the cornerite that inlet side 10, Exit-edge 12 turn in a circumferential direction
110o, uniform pitch section cornerite
get 30o.Inlet angle
βget 25 °, exit angle
α 0for 85o.
By the calculating of formula (2), uniform pitch section axial length
sfor 32mm, by the calculating of formula (5) and formula (8), order
=80o, x=L
1, obtain spiral vane variable pitch section axial length L
1be 222 mm, by the calculating of formula (5) and formula (9), order
=110o, x=L, then turbulent flow generator blade axial overall length
lbe 254 mm, through formula (1) checking computations,
lwithin span.
Value 0o, 10o, 20o respectively ..., 110o, by the calculating of formula (5), formula (8), formula (9), formula (3) and formula (4), the circulary cylindrical coordinates of the blade outer rim molded line (vane type line) 11 of the present embodiment is as shown in table 1:
Table 1 computational process table
Use the turbulent flow generator of the present invention's design, compared with other turbulent flow generator, have hydraulic efficiency high, the advantages such as shearing force is strong, and cavitation erosion performance is good, improve the middle concentration paper pulp conveying capacity of pump.Achieve the effect of Medium-Consistency Suspension fluidization and divided gas flow, solve middle concentration paper pulp for want of self mobility and gas holdup excessive and cause a conveying difficult problem.
Claims (1)
1. a turbulence generator for medium-consistency paper pulp pump, described turbulent flow generator is installed on pump impeller front end, be installed on same axle with pump impeller, turbulent flow generator is made up of wheel hub and the spiral vane be fixed on wheel hub, it is characterized in that: spiral vane is made up of inlet face, working surface, the back side, exit face and outer edge surface; Wherein working surface is three-dimensional space curved surface, is made up of inlet side, blade outer rim molded line and Exit-edge, and the back side is thickeied by working surface equal thickness and forms; Inlet side is perpendicular to axial direction, and Exit-edge is also perpendicular to axial direction, and inlet side, Exit-edge turn over an angle in a circumferential direction and form subtended angle of blade; The spiral vane external diameter of described turbulent flow generator
d 2get pump impeller blade inlet diameter, axial overall length
lits span is determined by formula (1); The helix molded line that described spiral vane outer rim molded line adopts variable pitch to combine with uniform pitch, inlet part adopts uniform pitch molded line, and exit portion adopts variable pitch molded line; The length of the medium pitch section of blade axial overall length
sdetermined by formula (2), in blade axial overall length, the length of variable pitch section is
l 1,
;
（1）；
（2）；
Wherein,
;
；
Described turbulent flow generator blade outer rim molded line is on the same cylndrical surface of line centered by hub axis, and the arbitrfary point on blade outer rim molded line often turns over angle relative to the outlet of blade outer rim molded line at circumferencial direction
time, the length that corresponding circumferencial direction launches is
y, the length that axial direction launches is
x, the length that the axial direction of corresponding variable pitch section launches is
x ', the length that the axial direction of uniform pitch section launches is
x ' ', and
x=x '+x ' ';
Blade outer rim molded line blade angle
α(
x) adopt piecewise function to represent, outlet variable pitch molded line blade angle is determined by formula (3), and import uniform pitch molded line blade angle is determined by formula (4);
，
（3）；
，
（4）；
The length that circumferencial direction launches
ydetermined by formula (5):
（5）；
For any point in blade outer rim molded line unfolded drawing, corresponding angle has:
（6）；
Formula (3) is substituted into formula (6), obtains variable pitch section circumferencial direction length of run
yrepresentation:
（7）；
Formula (7) is substituted into formula (5), obtains circumferencial direction and often turn over angle
length x ' the value of the axial direction expansion of time-varying pitch section:
（8）；
In like manner, formula (4) is substituted into formula (6), then substitutes into formula (5), obtain circumferencial direction and often turn over angle
time uniform pitch section the length launched of axial direction
x ' 'value:
(9);
Wherein:
qfor pump volume flow (m
3/ h);
ρfor Media density (kg/m
3);
nfor turbulent flow generator rotating speed (r/min);
ωfor turbulent flow generator angular velocity of rotation (rad/s), by
ω=30
π/ndetermine;
d h for turbulent flow generator hub diameter (m), get (0.2 ~ 0.4)
d 2;
v mfor media flow axial velocity (m/s);
afor the long-pending (m of turbulent flow generator cross section of fluid channel
2); Z is the turbulent flow generator number of blade, gets the half of pump impeller blade number;
δfor the vane thickness (m) of spiral vane, equal the vane thickness of pump impeller;
θfor uniform pitch section cornerite, get (1/4-1/3)
,
for the angle that inlet side and Exit-edge turn in a circumferential direction, i.e. subtended angle of blade, value is 90o-120o;
βfor the inlet angle of spiral vane outer rim molded line starting point, it is specially the angle between spiral vane outer rim molded line import tangent direction and circumferencial direction, gets 25 °;
α(
x) be blade outer rim molded line blade angle, it to be specially on blade outer rim molded line arbitrfary point tangent direction and by the angle between this circumferencial direction;
α 0for the exit angle of blade outer rim molded line terminal, it is specially the angle between blade outer rim molded line exit tangent direction and circumferencial direction,
α 0value is 85o – 90o; Described inlet face and the radius of exit face are all the half of spiral vane thickness; Described spiral vane launches along the axial direction of wheel hub, vertical with wheel hub; Spiral vane and wheel hub joint are with the arc transition of radius 10 ~ 40mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210095659.0A CN102619779B (en) | 2012-04-01 | 2012-04-01 | Turbulence generator for medium-consistency paper pulp pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210095659.0A CN102619779B (en) | 2012-04-01 | 2012-04-01 | Turbulence generator for medium-consistency paper pulp pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102619779A CN102619779A (en) | 2012-08-01 |
| CN102619779B true CN102619779B (en) | 2015-02-04 |
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ID=46559914
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210095659.0A Active CN102619779B (en) | 2012-04-01 | 2012-04-01 | Turbulence generator for medium-consistency paper pulp pump |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102817868B (en) * | 2012-08-09 | 2016-05-18 | 文树平 | A kind of eddy current type impeller of smoke exhaust ventilator |
| CN103615411A (en) * | 2013-12-05 | 2014-03-05 | 江苏飞跃机泵集团有限公司 | Flow guiding generator of medium concentration pulp pump |
| CN113019640B (en) * | 2021-03-29 | 2022-07-22 | 南京工程学院 | Efficient superhard ultramicro powder vertical hydraulic turbulent mill |
| CN113565574A (en) * | 2021-07-15 | 2021-10-29 | 江苏大学镇江流体工程装备技术研究院 | Anti-cavitation impeller of partial flow pump |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4826398A (en) * | 1987-07-06 | 1989-05-02 | Kamyr Ab | Medium consistency pump with self-feeding |
| FI111023B (en) * | 1998-12-30 | 2003-05-15 | Sulzer Pumpen Ag | Method and apparatus for pumping material and rotor used in connection with the apparatus |
| CN1851118A (en) * | 2006-05-30 | 2006-10-25 | 江苏大学 | Moderate high-thick paper pulp fluidifying apparatus |
| CN101413512A (en) * | 2008-11-17 | 2009-04-22 | 陈潜 | Spiral type self-absorbing paper pulp pump vane |
| CN101538811B (en) * | 2009-04-16 | 2011-05-25 | 中国计量学院 | Turbulent generator of medium-consistency pulp |
| CN201598531U (en) * | 2009-10-30 | 2010-10-06 | 杭州萧山美特轻工机械有限公司 | Impeller of turbulence generator with variable helix angle |
| CN201836059U (en) * | 2010-06-01 | 2011-05-18 | 杭州萧山美特轻工机械有限公司 | Turbulent medium-consistency stuff pump with variable helical angles |
| CN202789684U (en) * | 2012-04-01 | 2013-03-13 | 江苏大学 | Medium-consistency pulp pump turbulence generator |
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2012
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