CN109519393B - Method for calculating axial force of diagonal flow pump - Google Patents

Method for calculating axial force of diagonal flow pump Download PDF

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Publication number
CN109519393B
CN109519393B CN201811589852.3A CN201811589852A CN109519393B CN 109519393 B CN109519393 B CN 109519393B CN 201811589852 A CN201811589852 A CN 201811589852A CN 109519393 B CN109519393 B CN 109519393B
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impeller
pump
meter
axial
axial force
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CN109519393A (en
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付强
陈铭
王秀礼
朱荣生
余健恩
高鹏涛
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Jiangsu University
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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 invention relates to a method for calculating axial force of an oblique flow pump. The design working condition flow Q, the design working condition lift H, the design working condition rotating speed n and the impeller inlet diameter d of the given diagonal flow pump are obtained1bWidth of impeller blade inlet b1Diameter d of impeller outlet2bWidth of impeller outlet b2The axial force F borne by the rotor part of the diagonal flow pump is calculated according to the parametersax. The method has important significance for ensuring the design quality of the diagonal flow pump and ensuring the safe, stable and efficient operation of the diagonal flow pump.

Description

Method for calculating axial force of diagonal flow pump
Technical Field
The invention relates to an oblique flow pump, in particular to a method for calculating an axial force of an oblique flow pump.
Background
In operation of the pump, an axial force is exerted on the rotor which pulls the rotor axially. Therefore, it is necessary to try to eliminate or balance this axial force. So that the pump can work normally. The axial force acting on the pump rotor is composed of the following parts: 1) the axial force generated by the front cover plate and the rear cover plate of the impeller asymmetrically points to the direction of the suction inlet of the impeller; 2) the axial force caused by the structure factors such as the pillow block, the shaft end and the like, and the direction of the axial force depends on the specific situation; 3) axial forces caused by the weight of the rotor, related to the arrangement of the rotor; 4) a dynamic counter force, which is directed behind the impeller.
Chinese patent No. CN201610731350.4 discloses an on-line measuring device for axial force of pump, which comprises a main shaft, a bearing inner sleeve is mounted on the main shaft, a bearing outer sleeve is further sleeved outside the bearing inner sleeve, a thrust bearing is arranged between the bearing inner sleeve and the bearing outer sleeve, a sensor is mounted in the bearing body and is fastened on the bearing outer sleeve through screws, a cylindrical pin is arranged on one side of the sensor, and a non-porous end cover is arranged on the other side of the sensor. The cylindrical pin and the imperforate end cap prevent radial and axial movement of the sensor. An on-line measuring method for axial force of pump is also disclosed. The device and the method have the advantages that the signal capturing time interval is 0.05 second, the precision is high, the sensitivity is high, and the on-line measurement of the axial force of the pump can be accurately carried out.
The invention discloses a shield pump axial force detection device disclosed in the Chinese patent No. CN201420232410.4, wherein a connecting flange is arranged at one end of a shell, the connecting flange can connect the shell with a rear bearing body of a shield pump, two guide rails are symmetrically arranged in the shell along the axial direction of the shell, a transmission device is slidably connected on the guide rails, one end of the transmission device is connected with a front transmission shaft through a self-aligning bearing, the other end of the transmission device is in threaded connection with a rear transmission shaft, the tail end of the rear transmission shaft is in threaded connection with a stroke adjusting disc which is rotatably supported on the shell, the front end of the front transmission shaft is fixedly connected with a shaft head of a shield pump shaft through a connecting piece with threads at both ends, a long opening is further formed in the side surface of the shell, an axial measuring rod is fixedly connected with the transmission device through the long opening, and a dial indicator matched with the axial measuring rod.
The invention discloses a pump axial force tester, which comprises an oil cylinder body, a pressure regulating cover, a piston, an oil filling or air discharging plug, a sealing ring, a pressure gauge connecting pipe and a pressure gauge or a pressure relay, wherein the pressure gauge or the pressure relay is communicated with the inner cavity of the oil cylinder body through the pressure gauge connecting pipe and is mainly used for testing the axial force of a centrifugal pump and can also be used for testing the axial force of other similar mechanical equipment.
The existing method for measuring the axial force of the rotor component of the diagonal flow pump needs a plurality of measuring instruments, is high in cost, inconvenient to measure, time-consuming and labor-consuming, and has the main problem that an accurate calculating method is lacked in the existing method for measuring and calculating the axial force of the diagonal flow pump.
Disclosure of Invention
Aiming at the problems in the prior art, the invention provides a method for calculating the axial force of an oblique flow pump. The method has the advantages of strong practicability and convenient application, and has important significance for ensuring the design quality of the diagonal flow pump and ensuring the safe, stable and efficient operation of the diagonal flow pump.
The technical scheme adopted for achieving the purpose is as follows: the design working condition flow Q, the design working condition lift H, the design working condition rotating speed n and the impeller inlet diameter d of the given diagonal flow pump are obtained1bWidth of impeller blade inlet b1Diameter d of impeller outlet2bWidth of impeller outlet b2The axial force F borne by the rotor part of the diagonal flow pump is calculated according to the parametersaxThe method comprises the following specific steps:
(1) impeller inlet area A1The calculation formula of (2):
A1＝πd1bb1(1)
in the formula:
A1impeller inlet area, meter2；
d1b-impeller inlet diameter, meter;
b1-impeller blade inlet width, meter;
(2) impeller exit area A2The calculation formula of (2):
A2＝πd2bb2(2)
in the formula:
A2impeller exit area, meter2；
d2b-impeller exit diameter, meter;
b2-impeller exit width, meter;
(3) speed c of inlet axial plane of impeller blade1mThe calculation formula of (2):
Figure BDA0001919991470000021
in the formula:
c1m-impeller blade inlet axial surface velocity, m/s;
QLa-impeller flow over-current, rice3A/second;
fq-number of impeller intakes;
A1-leafArea of wheel inlet, rice2；
(4) Speed c of outlet axial plane of impeller blade2mThe calculation formula of (2):
Figure BDA0001919991470000022
in the formula:
c2m-impeller blade exit axial velocity, m/s;
QLa-impeller flow over-current, rice3A/second;
fq-number of impeller intakes;
A2impeller exit area, meter2；
(5) Impulsive force FIThe calculation formula of (2):
FI＝ρQ(c1m-c2mcose2) (5)
in the formula:
FI-impulsive force, cattle;
Q-Pump flow, meter3A/second;
rho-fluid density, kg/m3；
c1m-impeller blade inlet axial surface velocity, m/s;
c2m-impeller blade exit axial velocity, m/s;
ε2angle between intermediate flow line at impeller outlet and rotor axis, °
(6) Specific speed nqThe calculation formula of (2):
Figure BDA0001919991470000031
in the formula:
nq-specific speed;
n-pump speed, rpm;
Q-Pump flow, meter3A/second;
fq-number of impeller intakes;
h, pump head, rice;
(7) empirical coefficient fhaThe calculation formula of (2):
Figure BDA0001919991470000032
in the formula:
fha-an empirical coefficient;
nq-specific speed;
nq，Ref-reference specific speed;
(8) axial force F applied to impellerHyThe calculation formula of (2):
Figure BDA0001919991470000041
in the formula:
FHy-the axial force to which the impeller is subjected, ox;
rho-fluid density, kg/m3；
g-acceleration of gravity, m/s2；
H, pump head, rice;
fha-an empirical coefficient;
dsp-the diameter of the stoma ring, meter;
dDshoulder diameter, meter;
(9) unbalanced axial force F on pump shaftwThe calculation formula of (2):
Fw＝1/4πdD 2(pamb-p1) (9)
in the formula:
Fw-unbalanced axial forces on the pump shaft, newton;
dDshoulder diameter, meter;
p1-pump inlet pressure, pa;
pamb-pump installation ambient pressure, pa;
(10) axial force F applied to rotor partaxThe calculation formula of (2):
Fax＝FHy-F1+Fw+Fcoupl(10)
in the formula:
Fax-axial forces to which the rotor components are subjected, ox;
FHy-the axial force to which the impeller is subjected, ox;
FI-impulsive force, cattle;
Fw-unbalanced axial forces on the pump shaft, newton;
Fcoupl-axial forces to which the coupling is subjected, ox;
the invention has the beneficial effects that:
the calculation method can obtain a relatively perfect and accurate calculation method for the axial force of the diagonal flow pump. The method has important significance for ensuring the design quality of the diagonal flow pump and ensuring the safe, stable and efficient operation of the diagonal flow pump.
Drawings
FIG. 1 is an axial view of a diagonal flow pump.
Detailed description of the invention
The invention is further described with reference to the following figures and detailed description.
The invention determines a calculation formula of axial force of an oblique flow pump through the following formulas. In the embodiment, the design working condition flow Q, the design working condition lift H, the design working condition rotating speed n and the impeller inlet diameter d of the given diagonal flow pump are measured1bWidth of impeller blade inlet b1Diameter d of impeller outlet2bWidth of impeller outlet b2For calculating the axial force of an oblique-flow pump by several parameters, e.g. 15 m3Second, H4.55 m, n 171 rpm, d1b1.336 m, b10.673 m, d2b1.9 m, b20.627 m:
A1＝πd1bb1＝π·1.336·0.673＝2.825m2
A2＝πd2bb2＝π·1.9·0.627＝3.743m2
Figure BDA0001919991470000052
FI＝ρQ(c1m-c2mcosε2)＝1000·15·(5.310-4.008cos41°)＝34276N
Figure BDA0001919991470000053
Figure BDA0001919991470000054
Fw＝1/4πdD 2(pamb-p1)＝0.25π·1.3942·(100000-116523)＝-25218N
Fax＝FHy-F1+Fw+Fcoupl＝137307-34276-25218+50000＝127813N
the present invention is not limited to the above embodiments, and other embodiments and modifications within the scope of the present invention are also included.

Claims (5)

1. A method for calculating axial force of an oblique flow pump includes the steps of setting design working condition flow Q, design working condition lift H, design working condition rotating speed n and impeller inlet diameter d of the oblique flow pump1bWidth of impeller blade inlet b1Diameter d of impeller outlet2bWidth of impeller outlet b2Calculating the axial force F borne by the rotor component of the diagonal flow pumpaxThe method is characterized in that the method comprises the following steps of,
Fax＝FHy-FI+Fw+Fcoupl
in the formula:
Fax-turn roundAxial forces to which the sub-assembly is subjected, ox;
FHy-the axial force to which the impeller is subjected, ox;
FI-impulsive force, cattle;
Fw-unbalanced axial forces on the pump shaft, newton;
Fcoupl-axial forces to which the coupling is subjected, ox;
wherein, unbalanced axial force F on the pump shaftwThe calculation formula of (2): fw＝1/4πdD 2(pamb-p1)
In the formula:
Fw-unbalanced axial forces on the pump shaft, newton;
dDshoulder diameter, meter;
p1-pump inlet pressure, pa;
pamb-pump installation ambient pressure, pa;
wherein the impeller is subjected to an axial force FHyThe calculation formula of (2):
Figure FDA0002277255520000011
wherein f ishaIs an empirical coefficient; the calculation formula is as follows:
Figure FDA0002277255520000012
wherein n isqIs the specific rotating speed; the calculation formula is as follows:
in the formula:
FHy-the axial force to which the impeller is subjected, ox;
rho-fluid density, kg/m3；
g-acceleration of gravity, m/s2；
H, pump head, rice;
dsp-the diameter of the stoma ring, meter;
dDshoulder diameter, meter;
nq，Ref-reference specific speed;
n-pump speed, rpm;
Q-Pump flow, meter3A/second;
fq-number of impeller intakes;
h, pump head, rice;
wherein the impact force FIThe calculation formula of (2): fI＝ρQ(c1m-c2mcosε2)
In the formula:
FI-impulsive force, cattle;
Q-Pump flow, meter3A/second;
rho-fluid density, kg/m3；
c1m-impeller blade inlet axial surface velocity, m/s;
c2m-impeller blade exit axial velocity, m/s;
ε2-the angle between the intermediate flow line at the impeller exit and the rotor axis.
2. The method for calculating the axial force of the diagonal flow pump according to claim 1, wherein the method comprises the following steps: speed c of inlet axial plane of impeller blade1mThe calculation formula of (2):
Figure FDA0002277255520000021
in the formula:
c1m-impeller blade inlet axial surface velocity, m/s;
QLa-impeller flow over-current, rice3A/second;
fq-number of impeller intakes;
A1impeller inlet area, meter2。
3. The method for calculating the axial force of the diagonal flow pump according to claim 2, wherein the method comprises the following steps: impeller inlet area A1The calculation formula of (2):
A1＝πd1bb1
in the formula:
A1impeller inlet area, meter2；
d1b-impeller inlet diameter, meter;
b1impeller blade inlet width, meter.
4. The method for calculating the axial force of the diagonal flow pump according to claim 1, wherein the method comprises the following steps: speed c of outlet axial plane of impeller blade2mThe calculation formula of (2):
in the formula:
c2m-impeller blade exit axial velocity, m/s;
QLa-impeller flow over-current, rice3A/second;
fq-number of impeller intakes;
A2impeller exit area, meter2。
5. The method for calculating the axial force of the diagonal flow pump according to claim 4, wherein the method comprises the following steps: impeller exit area A2The calculation formula of (2):
A2＝πd2bb2
in the formula:
A2impeller exit area, meter2；
d2b-impeller exit diameter, meter;
b2impeller exit width, meter.
CN201811589852.3A 2018-12-25 2018-12-25 Method for calculating axial force of diagonal flow pump Active CN109519393B (en)

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CN110231114B (en) * 2019-04-24 2021-09-24 安徽昊星节能科技有限公司 Method for calculating axial force of ultra-low specific speed water turbine for cooling tower

Citations (8)

* Cited by examiner, † Cited by third party
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

Patent Citations (10)

* Cited by examiner, † Cited by third party
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

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