CN109519393A - A kind of calculation method of diagonal pumps axial force - Google Patents
A kind of calculation method of diagonal pumps axial force Download PDFInfo
- Publication number
- CN109519393A CN109519393A CN201811589852.3A CN201811589852A CN109519393A CN 109519393 A CN109519393 A CN 109519393A CN 201811589852 A CN201811589852 A CN 201811589852A CN 109519393 A CN109519393 A CN 109519393A
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- Prior art keywords
- impeller
- axial force
- rice
- formula
- diagonal pumps
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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
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0088—Testing machines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/007—Details, component parts, or accessories especially adapted for liquid pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Control Of Non-Positive-Displacement Pumps (AREA)
Abstract
The present invention relates to a kind of calculation methods of diagonal pumps axial force.Design conditions flow Q, design conditions lift H, the design conditions revolving speed n of given diagonal pumps, impeller inlet diameter d1b, impeller blade entrance width b1, impeller outlet diameter d2b, impeller outlet width b2Etc. several parameters, to calculate axial force F suffered by diagonal pumps rotor partax.To the designing quality for guaranteeing diagonal pumps, it is ensured that its safe and stable and efficient operation is of great significance.
Description
Technical field
The present invention relates to a kind of diagonal pumps, in particular to a kind of calculation method of diagonal pumps axial force.
Background technique
Pump in operation, acts on axial force on rotor, it is mobile which pulls on rotor axial.Therefore, it is necessary to try to disappear
Remove or balance this axial force.Pump can be made to work normally.The axial force acted on pump rotor is made of: 1) leaf following each section
The axial force that front and rear cover plate asymmetry generates is taken turns, this power is directed toward suction eye direction；2) structural factors such as axis platform, shaft end cause
Axial force, direction is depending on the circumstances；3) axial force caused by rotor weight, it is related with the arrangement of rotor；4) it moves anti-
Power, this power are directed toward impeller back face.
The Chinese invention patent that Patent No. CN201610731350.4 discloses a kind of pump axial force on-line measurement dress
Set, including main shaft, bearing inner sleeve be housed on main shaft, be also cased with bearing outside outside bearing inner sleeve, bearing inner sleeve and bearing outside it
Between be equipped with thrust bearing, sensor is installed in bearing body, and is fastened on bearing outside by screw, and sensor side is equipped with
Straight pin, another side senser are equipped with non-porous end cap.Straight pin and non-porous end cap can prevent sensor from generating radial and axial fortune
It is dynamic.Also disclose a kind of pump axial force On-line Measuring Method.The signal crawl time interval of the device and method is 0.05 second, essence
Degree is high, high sensitivity, can accurately carry out the on-line measurement of pump axial force.
A kind of shielding force at direction of pump spindle detection is disclosed in the Chinese invention patent that Patent No. CN201420232410.4
Device, one end of shell are provided with connecting flange, and connecting flange can connect the rear bearing body of shell and canned motor pump, in shell
Axially and symmetrically be arranged along it in vivo there are two guide rail, slidably connect transmission device on guide rail, one end of transmission device with
Front propeller shaft is connected by self-aligning bearing, and the other end of transmission device is threadedly coupled with inter-axle shaft, and the end of inter-axle shaft
It is threadedly coupled with the stroke adjustment disk being rotatably supported on shell, the front end of front propeller shaft passes through the threaded connector in both ends
It is fixedly connected with the spindle nose of shielding pump shaft, is also provided with long mouth in the side of shell, axially measured bar is filled by long mouth and transmission
It sets and is fixedly connected, the dial gauge to match with axially measured bar position is additionally provided with outside shell.
The Chinese invention patent that Patent No. CN201120184174.X discloses a kind of axial force test instrument for pump, including
Cylinder body, pressure regulating cover, piston, oiling or expanding plug, sealing ring and gauge manifold, pressure gauge or pressure switch composition,
Pressure gauge or pressure switch are connected with oil cylinder intracoelomic cavity by gauge manifold, and the survey of centrifugal pump axial force is mainly used for
Examination, can also be used for the test of other similar mechanical equipment axial forces, the axial force of rotor is acted on using pump operation, produces rotor
The machine driving of raw axial displacement, is converted into the hydraulic drive for pushing piston to execute, and increases oily in-cylinder pressure, is connected to oil cylinder
Pressure gauge Real time dynamic display axial force size and direction or monitoring is remotely shown by pressure switch.
The existing measurement for axial force suffered by diagonal pumps rotor part requires to use numerous measuring instruments, at high cost,
Measurement is inconvenient, takes time and effort, and the existing main problem of diagonal pumps axial force measuring and calculating at present is the absence of accurate calculating side
Method.
Summary of the invention
Aiming at the problems existing in the prior art, the present invention provides a kind of calculation methods of diagonal pumps axial force.It is practical
Property it is strong, using convenient, to the designing quality for guaranteeing diagonal pumps, it is ensured that its safe and stable and efficient operation is of great significance.
In order to realize purpose described above and used technical solution is: the design conditions flow Q of given diagonal pumps,
Design conditions lift H, design conditions revolving speed n, impeller inlet diameter d1b, impeller blade entrance width b1, impeller outlet diameter d2b,
Impeller outlet width b2Etc. several parameters, to calculate axial force F suffered by diagonal pumps rotor partax, the specific steps are as follows:
(1) impeller inlet area A1Calculation formula:
A1=π d1bb1 (1)
In formula:
A1- impeller inlet area, rice2；
d1b- impeller inlet diameter, rice；
b1- impeller blade entrance width, rice；
(2) impeller outlet area A2Calculation formula:
A2=π d2bb2 (2)
In formula:
A2- impeller outlet area, rice2；
d2b- impeller outlet diameter, rice；
b2- impeller outlet width, rice；
(3) impeller blade import axis plane velocity c1mCalculation formula:
In formula:
c1m- impeller blade import axis plane velocity, meter per second；
QLa- impeller overcurrent flow, rice3/ the second；
fq- impeller inlet number；
A1- impeller inlet area, rice2；
(4) impeller blade exports axis plane velocity c2mCalculation formula:
In formula:
c2m- impeller blade exports axis plane velocity, meter per second；
QLa- impeller overcurrent flow, rice3/ the second；
fq- impeller inlet number；
A2- impeller outlet area, rice2；
(5) impulse force FICalculation formula:
FI=ρ Q (c1m-c2mcosε2) (5)
In formula:
FI- impulse force, ox；
Q-pump discharge, rice3/ the second；
ρ-fluid density, kg/m3；
c1m- impeller blade import axis plane velocity, meter per second；
c2m- impeller blade exports axis plane velocity, meter per second；
ε2The angle between center line of flow path and armature spindle at-impeller outlet, °
(6) specific speed nqCalculation formula:
In formula:
nq- specific speed；
N-revolution speed, rev/min；
Q-pump discharge, rice3/ the second；
fq- impeller inlet number；
H-pump lift, rice；
(7) empirical coefficient fhaCalculation formula:
In formula:
fha- empirical coefficient；
nq- specific speed；
nQ, Ref- refer to specific speed；
(8) axial force F suffered by impellerHyCalculation formula:
In formula:
FHyAxial force suffered by-impeller, ox；
ρ-fluid density, kg/m3；
G-acceleration of gravity, meter per second2；
H-pump lift, rice；
fha- empirical coefficient；
dsp- choma diameter, rice；
dD- shaft shoulder diameter, rice；
(9) non-equilibrium axial force F on pump shaftwCalculation formula:
Fw=1/4 π dD 2(pamb-p1) (9)
In formula:
FwNon-equilibrium axial force, ox on-pump shaft；
dD- shaft shoulder diameter, rice；
p1- pump inlet pressure, pa；
pamb- pump installation environment pressure, pa；
(10) axial force F suffered by rotor partaxCalculation formula:
Fax=FHy-F1+Fw+Fcoupl (10)
In formula:
FaxAxial force suffered by-rotor part, ox；
FHyAxial force suffered by-impeller, ox；
FI- impulse force, ox；
FwNon-equilibrium axial force, ox on-pump shaft；
FcouplAxial force suffered by-shaft coupling, ox；
The invention has the benefit that
The accurate diagonal pumps Axial Force Calculating method of the available comparatively perfect of calculation method of the present invention.To guarantee
The designing quality of diagonal pumps, it is ensured that its safe and stable and efficient operation is of great significance.
Detailed description of the invention
Fig. 1 is the axial plane figure of diagonal pumps.
Specific implementation method
The present invention is further described with reference to the accompanying drawings and detailed description.
The present invention determines a kind of calculation formula of diagonal pumps axial force by following formula.This embodiment be to
Determine the design conditions flow Q, design conditions lift H, design conditions revolving speed n of diagonal pumps, impeller inlet diameter d1b, impeller blade into
Mouth width degree b1, impeller outlet diameter d2b, impeller outlet width b2The axial force of diagonal pumps, such as Q are calculated etc. several parameters
=15 meters3/ the second, H=4.55 meters, n=171 revs/min, d1b=1.336 meters, b1=0.673 meter, d2b=1.9 meters, b2=
0.627 meter:
A1=π d1bb1=π 1.3360.673=2.825m2
A2=π d2bb2=π 1.90.627=3.743m2
FI=ρ Q (c1m-c2mcos ε 2)=100015 (5.310-4.008cos41 °)=34276N
Fw=1/4 π dD 2(pamb-p1The π of)=0.25 1.3942(100000-116523)=- 25218N
Fax=FHy-F1+Fw+Fcoupl=137307-34276-25218+50000=127813N
The above-mentioned detailed description made for the invention patent referring to embodiment, but the invention is not limited to above realities
Example is applied, also includes other embodiments and variation within the scope of present inventive concept.
Claims (8)
1. a kind of calculation method of diagonal pumps axial force gives the design conditions flow Q, design conditions lift H, design of diagonal pumps
Operating condition revolving speed n, impeller inlet diameter d1b, impeller blade entrance width b1, impeller outlet diameter d2b, impeller outlet width b2, come
Calculate axial force F suffered by diagonal pumps rotor partax, which is characterized in that
Fax=FHy-FI+Fw+Fcoupl
In formula:
FaxAxial force suffered by-rotor part, ox；
FHyAxial force suffered by-impeller, ox；
FI- impulse force, ox；
FwNon-equilibrium axial force, ox on-pump shaft；
FcouplAxial force suffered by-shaft coupling, ox.
2. a kind of calculation method of diagonal pumps axial force according to claim 1, which is characterized in that non-equilibrium axis on pump shaft
To power FwCalculation formula: Fw=1/4 π dD 2(pamb-p1)
In formula:
FwNon-equilibrium axial force, ox on-pump shaft；
dD- shaft shoulder diameter, rice；
p1- pump inlet pressure, pa；
pamb- pump installation environment pressure, pa.
3. a kind of calculation method of diagonal pumps axial force according to claim 1, which is characterized in that axial force suffered by impeller
FHyCalculation formula:
Wherein, fhaFor empirical coefficient；Calculation formula are as follows:
Wherein, nqFor specific speed；Calculation formula are as follows:
In formula:
FHyAxial force suffered by-impeller, ox；
ρ-fluid density, kg/m3；
G-acceleration of gravity, meter per second2；
H-pump lift, rice；
dsp- choma diameter, rice；
dD- shaft shoulder diameter, rice；
nQ, Ref- refer to specific speed；
N-revolution speed, rev/min；
Q-pump discharge, rice3/ the second；
fq- impeller inlet number；
H-pump lift, rice.
4. a kind of calculation method of diagonal pumps axial force according to claim 1, which is characterized in that impulse force FICalculating it is public
Formula: FI=ρ Q (c1m-c2mcosε2)
In formula:
FI- impulse force, ox；
Q-pump discharge, rice3/ the second；
ρ-fluid density, kg/m3；
c1m- impeller blade import axis plane velocity, meter per second；
c2m- impeller blade exports axis plane velocity, meter per second；
ε2The angle between center line of flow path and armature spindle at-impeller outlet, °.
5. a kind of calculation method of diagonal pumps axial force according to claim 4, it is characterised in that: impeller blade import axis
Face velocity c1mCalculation formula:
In formula:
c1m- impeller blade import axis plane velocity, meter per second；
QLa- impeller overcurrent flow, rice3/ the second；
fq- impeller inlet number；
A1- impeller inlet area, rice2。
6. a kind of calculation method of diagonal pumps axial force according to claim 5, it is characterised in that: impeller inlet area A1
Calculation formula:
A1=π d1bb1
In formula:
A1- impeller inlet area, rice2；
d1b- impeller inlet diameter, rice；
b1- impeller blade entrance width, rice.
7. a kind of calculation method of diagonal pumps axial force according to claim 4, it is characterised in that: impeller blade exports axis
Face velocity c2mCalculation formula:
In formula:
c2m- impeller blade exports axis plane velocity, meter per second；
QLa- impeller overcurrent flow, rice3/ the second；
fq- impeller inlet number；
A2- impeller outlet area, rice2。
8. a kind of calculation method of diagonal pumps axial force according to claim 7, it is characterised in that: impeller outlet area A2
Calculation formula:
A2=π d2bb2
In formula:
A2- impeller outlet area, rice2；
d2b- impeller outlet diameter, rice；
b2- impeller outlet width, rice.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811589852.3A CN109519393B (en) | 2018-12-25 | 2018-12-25 | Method for calculating axial force of diagonal flow pump |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811589852.3A CN109519393B (en) | 2018-12-25 | 2018-12-25 | Method for calculating axial force of diagonal flow pump |
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| Publication Number | Publication Date |
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| CN109519393A true CN109519393A (en) | 2019-03-26 |
| CN109519393B CN109519393B (en) | 2020-02-21 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201811589852.3A Active CN109519393B (en) | 2018-12-25 | 2018-12-25 | Method for calculating axial force of diagonal flow pump |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110231114A (en) * | 2019-04-24 | 2019-09-13 | 安徽昊星节能科技有限公司 | Ultra-low specific speed hydraulic turbine axial force calculation method used for cooling tower |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU885626A2 (en) * | 1980-03-25 | 1981-11-30 | За витель | Centrifugal pump |
| CN87203854U (en) * | 1987-03-21 | 1987-12-26 | 郭宝权 | Centrifugal pump impeller capable of automatic balancing axial force |
| DE3330364C2 (en) * | 1983-08-23 | 1989-06-15 | Ksb Aktiengesellschaft, 6710 Frankenthal, De | |
| GB2298901A (en) * | 1995-03-17 | 1996-09-18 | Aisin Seiki | Gas turbine engine axial thrust balancing |
| CN102251991A (en) * | 2011-08-19 | 2011-11-23 | 江苏大学 | Axial force balance device and method for shield pump |
| CN104613003A (en) * | 2014-11-26 | 2015-05-13 | 江苏大学 | Hydraulic design method for low-specific-speed overload-free centrifugal pump impeller |
| CN107013472A (en) * | 2017-04-18 | 2017-08-04 | 江苏大学 | It is a kind of to measure the method that pump chamber size influences on centrifugal pump external characteristics and axial force |
| CN207406495U (en) * | 2017-10-20 | 2018-05-25 | 大连环友屏蔽泵有限公司 | A kind of canned motor pump with axial force balance auxiliary device |
-
2018
- 2018-12-25 CN CN201811589852.3A patent/CN109519393B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU885626A2 (en) * | 1980-03-25 | 1981-11-30 | За витель | Centrifugal pump |
| DE3330364C2 (en) * | 1983-08-23 | 1989-06-15 | Ksb Aktiengesellschaft, 6710 Frankenthal, De | |
| CN87203854U (en) * | 1987-03-21 | 1987-12-26 | 郭宝权 | Centrifugal pump impeller capable of automatic balancing axial force |
| GB2298901A (en) * | 1995-03-17 | 1996-09-18 | Aisin Seiki | Gas turbine engine axial thrust balancing |
| CN102251991A (en) * | 2011-08-19 | 2011-11-23 | 江苏大学 | Axial force balance device and method for shield pump |
| CN102251991B (en) * | 2011-08-19 | 2014-05-28 | 江苏大学 | Axial force balance device and method for shield pump |
| CN104613003A (en) * | 2014-11-26 | 2015-05-13 | 江苏大学 | Hydraulic design method for low-specific-speed overload-free centrifugal pump impeller |
| CN104613003B (en) * | 2014-11-26 | 2017-05-03 | 江苏大学 | Hydraulic design method for low-specific-speed overload-free centrifugal pump impeller |
| CN107013472A (en) * | 2017-04-18 | 2017-08-04 | 江苏大学 | It is a kind of to measure the method that pump chamber size influences on centrifugal pump external characteristics and axial force |
| CN207406495U (en) * | 2017-10-20 | 2018-05-25 | 大连环友屏蔽泵有限公司 | A kind of canned motor pump with axial force balance auxiliary device |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110231114A (en) * | 2019-04-24 | 2019-09-13 | 安徽昊星节能科技有限公司 | Ultra-low specific speed hydraulic turbine axial force calculation method used for cooling tower |
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| CN109519393B (en) | 2020-02-21 |
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