CN101749277B - Method for reducing lift of closing point of condensate pump - Google Patents
Method for reducing lift of closing point of condensate pump Download PDFInfo
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- CN101749277B CN101749277B CN2008102292704A CN200810229270A CN101749277B CN 101749277 B CN101749277 B CN 101749277B CN 2008102292704 A CN2008102292704 A CN 2008102292704A CN 200810229270 A CN200810229270 A CN 200810229270A CN 101749277 B CN101749277 B CN 101749277B
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Abstract
The invention relates to lift of a closing point which affects the pressure grade of a condensate pump, in particular to a method for reducing the lift of the closing point of the condensate pump, and the method comprises the following steps: increasing the width of an outlet of an impeller of the condensate pump, and increasing the area of an inlet of a pump bowl, thereby increasing the flow rate of the condensate pump, leading a lift curve of the condensate pump to tend to be smooth, reducing the lift of the closing point and leading a pipeline system of the condensate pump to select the lower pressure grade. The method only changes the shapes of individual parts without changing the structure of the pump; the method is simple, easy to realize and strong in operatability; and the method can reduce the lift of the closing point under the premise of not increasing the manufacturing cost and have better technical and economic effects.
Description
Technical field
The present invention relates to influence the lift of closing point of condensate pump pressure rating, specifically a kind of method that reduces lift of closing point of condensate pump.
Background technique
According to the centrifugal water pump curve, when flow diminished, lift raise; When flow became 0, lift reached peak, was lift of closing point this moment.
According to power plant's design system pressure demand, if the outlet pressure value of water pump is 3.3MPa, the pressure rating of decision pipeline then is 4.0MPa.If the lift of closing point of water pump is higher than 4.0MPa, whole pipe-line system just will be brought up to next pressure rating, i.e. 6.4MPa; The pipeline of whole system, valve, instrument etc. all will be selected according to next pressure rating like this, and engineering cost will increase greatly.
The lift ratio of present closing point of condensate pump and design point is about 1.3, and the market primary demand is 1.2, the requirement that has even lower.Therefore, guaranteeing under the constant situation of other performance of condensate pump that how ratio is reduced to below 1.2 by present 1.3, the lift of closing point that reduces condensate pump has as requested become problem demanding prompt solution.
Summary of the invention
In order to address the above problem, the object of the present invention is to provide a kind of method that reduces lift of closing point of condensate pump, promptly reduce the pass close point of condensate pump and the pressure ratio of design point.
The objective of the invention is to realize through following technological scheme:
Method of the present invention is: the impeller outlet width of condensate pump is strengthened; The inlet area of blower inlet casing increases, and the flow of condensate pump is increased, and the head curve of condensate pump tends towards stability; Lift of closing point reduces, and the pipe-line system of condensate pump can be selected low one pressure rating.
Wherein: strengthen impeller outlet width and be specially:
1). keep lift constant, with impeller initial flow Q
mBe amplified to Q, according to formula
Calculate scale factor λ; Q wherein
mBe the initial flow of impeller, Q is the flow after impeller amplifies, n
mBe the initial speed of impeller, n is the rotating speed behind the impeller amplified flow, D
mBe the impeller initial diameter, D is the diameter after impeller strengthens exit width;
2). again with the initial exit width b of impeller
2' increase λ doubly, draw the impeller outlet width b after the increasing
2, i.e. b
2=λ b
2';
3). the initial exit width b of impeller
2λ times of ' increase, correspondingly the original width b of impeller eye
1' also increase λ doubly, draw the impeller eye width b after the increasing
1, i.e. b
1=λ b
1';
4). after the gateway width of impeller increased, the back shroud of impeller and the size constancy of wheel hub extended to the front shroud size positions after the expansion with front shroud of impeller forward by original dimension, have strengthened the exit width of impeller.
Impeller eye width after actual the increasing is slightly less than through formula b
1=λ b
1Impeller eye width b after the ' increasing that calculates
1, can confirm according to the structure of impeller eye.
Increasing the blower inlet casing inlet area is specially:
1). through the initial inlet outer diameter D of blower inlet casing
1And inlet inner diameter D
2, calculate blower inlet casing inlet area S
1,
2). according to the initial flow Q of impeller
mReach the flow Q after impeller amplifies, calculate the increase multiple k=Q/Q of flow
m
3). with the inlet area S of blower inlet casing
1Increase k doubly, the blower inlet casing inlet area S after promptly increasing
2=kS
1
4). keep the inboard molded lines of blower inlet casing runner inlet constant, i.e. D
2Constant, outwards expand outside molded lines, the blower inlet casing inlet outer diameter after the expansion is D
Outward, according to the annulus area formula
Can calculate the blower inlet casing inlet outer diameter after the expansion
The inlet outer diameter D that blower inlet casing is initial
1Expand to D
Outward, increased the inlet area of blower inlet casing.
Increasing the blower inlet casing inlet area is specially:
1). through the initial inlet outer diameter D of blower inlet casing
1And inlet inner diameter D
2, calculate blower inlet casing inlet area S
1,
2). according to the initial flow Q of impeller
mReach the flow Q after impeller amplifies, calculate the increase multiple k=Q/Q of flow
m
3). with the inlet area S of blower inlet casing
1Increase k doubly, the blower inlet casing inlet area S after promptly increasing
2=kS
1
4). the diameter at blower inlet casing runner inlet center is D, D=(D
1+ D
2)/2 are that D is the center with the diameter at blower inlet casing runner inlet center, and its outside is respectively S with inboard area
OutwardAnd S
In,
5). according to the blower inlet casing inlet area S after increasing
2And the initial inlet area S of blower inlet casing
1, calculate runner inlet area net increase part S ', S '=S
2-S
1
6). S ' adds respectively in initial inside and outside lateral area ratio with runner inlet area net increase part, and the outside area
behind the increase area increases the outside diameter
behind inboard area
the increase area behind outside diameter
the increase area behind the area
7). keep blower inlet casing center line of suction position motionless, respectively to inside and outside both direction expanded channel molded lines, i.e. the initial inlet outer diameter D of blower inlet casing
1Outwards expand to D
Outward, the inlet inner diameter D that blower inlet casing is initial
2Inwardly expand to D
In, increased the inlet area of blower inlet casing.
Advantage of the present invention and good effect are:
1. the inventive method need not to change the structure of pump itself, and just changes the shape of individual parts, and method is simple, realizes easily, and is workable.
2. the inventive method has realized the reduction of lift of closing point under the prerequisite that does not increase manufacture cost, has better techno-economic effect.
Description of drawings
Fig. 1 is the condensate pump performance chart;
Fig. 2 is for adopting the performance chart after the inventive method reduces lift of closing point of condensate pump;
Fig. 3 is the impeller axial plane figure behind impeller original state and the increasing exit width;
Fig. 4 is a kind of blower inlet casing original state and the blower inlet casing molded lines that is added to after the open area;
Fig. 5 is another kind of blower inlet casing original state and the blower inlet casing molded lines that is added to after the open area;
Fig. 6 is the overall structure schematic representation of condensate pump.
Embodiment
Below in conjunction with accompanying drawing the present invention is made further detailed description.
As shown in Figure 1, A is the initial model curve of model pump, utilizes the inventive method that the initial model curve is drawn close to aim curve B, reduces the lift of closing point of condensate pump.Method of the present invention is the impeller outlet width increasing with condensate pump; The inlet area of blower inlet casing increases, and the flow of condensate pump is increased, and the head curve of condensate pump tends towards stability; Lift of closing point reduces, and the pipe-line system of condensate pump can be selected low one pressure rating; The initial model curve A become curve A ', as shown in Figure 2; Then, reduce the one-level impeller, curve A ' promptly the become curve A approaching " with aim curve B.
The inventive method is specially:
One, strengthen impeller outlet width:
1). the initial flow Q of impeller 10
m=1500m
3During/h, the lift that this flow point is corresponding is H=320m, matches with aim curve for making its model curve trend, and its flow is amplified to Q=1700m
3/ h is according to formula
Calculate scale factor λ, wherein the initial flow Q of impeller
m=1500m
3/ h, the flow Q=1700m after impeller amplifies
3/ h, the initial speed n of impeller
m=1480rpm, the rotation speed n=1480rpm behind the impeller amplified flow, D
mBe the impeller initial diameter, D is the diameter after impeller strengthens exit width, so,
2). keep lift constant, only increase flow, so again with the initial exit width b of impeller 10
2' increase λ doubly, draw the impeller outlet width b after the increasing
2, i.e. b
2=λ b
2'; The initial exit width b of the impeller of model pump
2'=59mm, the impeller outlet width b after the increasing
2=λ b
2'=1.0426 * 59=61.5mm;
3). the initial exit width b of impeller
2λ times of ' increase, correspondingly the original width b of impeller eye
1' also increase λ doubly, draw the impeller eye width b after the increasing
1, i.e. b
1=λ b
1'; If throat width converts according to above-mentioned λ, then can reach 315mm, consider that the inlet area increasing may cause liquid return, influence the suction performance of impeller, the impeller eye width outline after actual the increasing is less than passing through formula b
1=λ b
1Impeller eye width b after the ' increasing that calculates
1Concrete numerical value can confirm that present embodiment impeller eye width only is increased to 307mm according to the structure of impeller eye, moves the front shroud size on correspondingly simultaneously; Blade shape is constant; The impeller width extends to the position that enlarges back front shroud 2 forward by the position of initial front shroud 1, and the size constancy of back shroud 3 and wheel hub 4 is as shown in Figure 3;
Two, increase blower inlet casing 8 inlet areas:
1). through the initial inlet outer diameter D of blower inlet casing
1And inlet inner diameter D
2, calculate blower inlet casing inlet area S
1,
The initial inlet outer diameter D of model pump blower inlet casing
1=725mm, the initial inlet outer diameter D of model pump blower inlet casing
2=613mm, the blower inlet casing inlet area
2). according to the initial flow Q of impeller
mReach the flow Q after impeller amplifies, calculate the increase multiple k=Q/Q of flow
mK=Q/Q
m=1700/1500=1.13;
3). with the inlet area S of blower inlet casing
1Increase k doubly, the blower inlet casing inlet area S after promptly increasing
2=kS
1S
2=kS
1=1.13 * 117696=132996mm
2
4). keep the inboard molded lines 5 of blower inlet casing runner inlet constant, i.e. D
2Constant, the outside molded lines 6 of blower inlet casing runner inlet is outwards extended to the outside molded lines 7 of the blower inlet casing runner after the expansion, the blower inlet casing inlet outer diameter after the expansion is D
Outward, according to the annulus area formula
Can calculate the blower inlet casing inlet outer diameter after the expansion
With D
2=613mm, S
2=132996mm
2The substitution following formula can get
The inlet outer diameter D that the model pump blower inlet casing is initial
1Expand to D
Outward, increased the inlet area of blower inlet casing, as shown in Figure 4.
One, strengthen impeller outlet width:
The increasing impeller outlet width method of present embodiment is identical with embodiment 1.
Two, increase blower inlet casing 8 inlet areas:
1). through the initial inlet outer diameter D of blower inlet casing
1And inlet inner diameter D
2, calculate blower inlet casing inlet area S
1,
The initial inlet outer diameter D of model pump blower inlet casing
1=725mm, the initial inlet outer diameter D of model pump blower inlet casing
2=613mm, the blower inlet casing inlet area
2). according to the initial flow Q of impeller
mReach the flow Q after impeller amplifies, calculate the increase multiple k=Q/Q of flow
mK=Q/Q
m=1700/1500=1.13;
3). with the inlet area S of blower inlet casing
1Increase k doubly, the blower inlet casing inlet area S after promptly increasing
2=kS
1S
2=kS
1=1.13 * 117696=132996mm
2
4). the diameter at blower inlet casing runner inlet center is D, D=(D
1+ D
2)/2=(725+613)/2=669mm is that D is the center with the diameter at blower inlet casing runner inlet center, and its outside is respectively S with inboard area
OutwardAnd S
In,
5). according to S
2And S
1, calculate runner inlet area net increase part S ', S '=S
2-S
1=132996-117696=15300mm
2
6). S ' adds respectively in initial inside and outside lateral area ratio with runner inlet area net increase part, the outside area behind the increase area
7). keep blower inlet casing center line of suction position motionless, the medial and lateral molded lines 5,6 of blower inlet casing runner inlet is the medial and lateral molded lines 9,7 of the blower inlet casing runner after inside and outside both direction extends to expansion, the i.e. initial inlet outer diameter D of blower inlet casing respectively
1Outwards expand to D
Outward, the inlet inner diameter D that blower inlet casing is initial
2Inwardly expand to D
In, increased the inlet area of blower inlet casing, as shown in Figure 5.
Through embodiment 1,2,, can calculate the lift of closing point of target pump and the ratio K of design point lift according to model pump performance test record and curve:
The lift of closing point H of target pump wherein
Close=385.4m, so the design point lift H=325.2m of target pump is K=H
Close/ H=385.4/325.2=1.185.
The lift of closing point H of model pump
Close=455.5m, the design point lift H=344.1m of model pump, its ratio K
0=H
Close/ H=455.5/344.1=1.324.
The lift of closing point of target pump and design point lift odds ratio master mould pump have descended 11.7%, and be visible, be feasible thereby make it through the runner that improves impeller and blower inlet casing to the scheme that big flow excursion reduces lift of closing point, and effect is apparent in view.
Table one: the technical parameter of target pump and model pump such as following table:
| Project | The technical parameter of target pump | The technical parameter of model pump |
| Flow Q (m 3/h) | 1480 | 1500 |
| Lift H (m) | 340 | 339 |
| Rotation speed n (rpm) | 1480 | 1480 |
| Efficiency eta (%) | 84 | 84 |
| Net positive suction head NPSHr (m) | 4.4 | 4.4 |
| Air horsepower N (kW) | 1684 | 1648 |
| Wear power P (kW) | 2000 | 2000 |
| Lift of closing point H Close(m) | 392 | 455 |
Claims (4)
1. method that reduces lift of closing point of condensate pump; It is characterized in that: the impeller outlet width of condensate pump is strengthened; The inlet area of blower inlet casing increases, and the flow of condensate pump is increased, and the head curve of condensate pump tends towards stability; Lift of closing point reduces, and the pipe-line system of condensate pump can be selected low one pressure rating;
Said increasing impeller outlet width is specially:
1). keep lift constant, with impeller initial flow Q
mBe amplified to Q, according to formula
Calculate scale factor λ; Q wherein
mBe the initial flow of impeller, Q is the flow after impeller amplifies, n
mBe the initial speed of impeller, n is the rotating speed behind the impeller amplified flow, D
mBe the impeller initial diameter, D is the diameter after impeller strengthens exit width;
2). again with the initial exit width b of impeller
2' increase λ doubly, draw the impeller outlet width b after the increasing
2, i.e. b
2=λ b
2';
3). the initial exit width b of impeller
2λ times of ' increase, correspondingly the original width b of impeller eye
1' also increase λ doubly, draw the impeller eye width b after the increasing
1, i.e. b
1=λ b
1';
4). after the gateway width of impeller increased, the back shroud of impeller and the size constancy of wheel hub extended to the front shroud size positions after the expansion with front shroud of impeller forward by original dimension, have strengthened the exit width of impeller;
Said increase blower inlet casing inlet area is specially:
1). through the initial inlet outer diameter D of blower inlet casing
1And inlet inner diameter D
2, calculate blower inlet casing inlet area S
1,
2). according to the initial flow Q of impeller
mReach the flow Q after impeller amplifies, calculate the increase multiple k=Q/Q of flow
m
3). with the inlet area S of blower inlet casing
1Increase k doubly, the blower inlet casing inlet area S after promptly increasing
2=kS
1
4). keep the inboard molded lines of blower inlet casing runner inlet constant, i.e. D
2Constant, outwards expand outside molded lines, the blower inlet casing inlet outer diameter after the expansion is D
Outward, according to the annulus area formula
Can calculate the blower inlet casing inlet outer diameter after the expansion
The inlet outer diameter D that blower inlet casing is initial
1Expand to D
Outward, increased the inlet area of blower inlet casing.
2. by the method for the described reduction lift of closing point of condensate pump of claim 1, it is characterized in that: the impeller eye width after said actual the increasing is slightly less than through formula b
1=λ b
1Impeller eye width b after the ' increasing that calculates
1, can confirm according to the structure of impeller eye.
3. method that reduces lift of closing point of condensate pump; It is characterized in that: the impeller outlet width of condensate pump is strengthened; The inlet area of blower inlet casing increases, and the flow of condensate pump is increased, and the head curve of condensate pump tends towards stability; Lift of closing point reduces, and the pipe-line system of condensate pump can be selected low one pressure rating;
Said increasing impeller outlet width is specially:
1). keep lift constant, with impeller initial flow Q
mBe amplified to Q, according to formula
Calculate scale factor λ; Q wherein
mBe the initial flow of impeller, Q is the flow after impeller amplifies, n
mBe the initial speed of impeller, n is the rotating speed behind the impeller amplified flow, D
mBe the impeller initial diameter, D is the diameter after impeller strengthens exit width;
2). again with the initial exit width b of impeller
2' increase λ doubly, draw the impeller outlet width b after the increasing
2, i.e. b
2=λ b
2';
3). the initial exit width b of impeller
2λ times of ' increase, correspondingly the original width b of impeller eye
1' also increase λ doubly, draw the impeller eye width b after the increasing
1, i.e. b
1=λ b
1';
4). after the gateway width of impeller increased, the back shroud of impeller and the size constancy of wheel hub extended to the front shroud size positions after the expansion with front shroud of impeller forward by original dimension, have strengthened the exit width of impeller;
Said increase blower inlet casing inlet area is specially:
1). through the initial inlet outer diameter D of blower inlet casing
1And inlet inner diameter D
2, calculate blower inlet casing inlet area S
1,
2). according to the initial flow Q of impeller
mReach the flow Q after impeller amplifies, calculate the increase multiple k=Q/Q of flow
m
3). with the inlet area S of blower inlet casing
1Increase k doubly, the blower inlet casing inlet area S after promptly increasing
2=kS
1
4). the diameter at blower inlet casing runner inlet center is D, D=(D
1+ D
2)/2 are the center with the diameter D at blower inlet casing runner inlet center, and its outside is respectively S with inboard area
OutwardAnd S
In,
5). according to the blower inlet casing inlet area S after increasing
2And the initial inlet area S of blower inlet casing
1, calculate runner inlet area net increase part S ', S '=S
2-S
1
6). S ' adds respectively in initial inside and outside lateral area ratio with runner inlet area net increase part, and the outside area
behind the increase area increases the outside diameter
behind inboard area
the increase area behind outside diameter
the increase area behind the area
7). keep blower inlet casing center line of suction position motionless, respectively to inside and outside both direction expanded channel molded lines, i.e. the initial inlet outer diameter D of blower inlet casing
1Outwards expand to D
Outward, the inlet inner diameter D that blower inlet casing is initial
2Inwardly expand to D
In, increased the inlet area of blower inlet casing.
4. by the method for the described reduction lift of closing point of condensate pump of claim 3, it is characterized in that: the impeller eye width after said actual the increasing is slightly less than through formula b
1=λ b
1Impeller eye width b after the ' increasing that calculates
1, can confirm according to the structure of impeller eye.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2008102292704A CN101749277B (en) | 2008-12-03 | 2008-12-03 | Method for reducing lift of closing point of condensate pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2008102292704A CN101749277B (en) | 2008-12-03 | 2008-12-03 | Method for reducing lift of closing point of condensate pump |
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| Publication Number | Publication Date |
|---|---|
| CN101749277A CN101749277A (en) | 2010-06-23 |
| CN101749277B true CN101749277B (en) | 2012-04-18 |
Family
ID=42476751
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|---|---|---|---|
| CN2008102292704A Active CN101749277B (en) | 2008-12-03 | 2008-12-03 | Method for reducing lift of closing point of condensate pump |
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|---|---|---|---|---|
| CN108664702B (en) * | 2018-04-10 | 2022-07-05 | 中国计量大学 | Method for increasing design point lift of multi-stage centrifugal condensate pump |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2349395Y (en) * | 1998-08-20 | 1999-11-17 | 山东中实电力科技总公司 | High-efficient inclained flow type water pump impeller |
| CN1580577A (en) * | 2004-05-19 | 2005-02-16 | 江苏大学 | Method for designing low-rate revolution centrifugal pump impeller |
-
2008
- 2008-12-03 CN CN2008102292704A patent/CN101749277B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2349395Y (en) * | 1998-08-20 | 1999-11-17 | 山东中实电力科技总公司 | High-efficient inclained flow type water pump impeller |
| CN1580577A (en) * | 2004-05-19 | 2005-02-16 | 江苏大学 | Method for designing low-rate revolution centrifugal pump impeller |
Non-Patent Citations (4)
| Title |
|---|
| JP昭58-187597A 1983.11.01 |
| 姜宜晋.离心泵叶轮尺寸偏差对泵的性能影响.《山西化工》.1995,(第04期),22,23,27. * |
| 袁寿其.水泵偏大流量设计方法的探讨.《排灌机械》.1988,(第01期),4-8. * |
| 袁建平 等.大型双吸泵机组性能优化研究.《中国农村水利水电》.2007,(第03期),93-96. * |
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