CN1811190A - Dynamic regulation method of axial force in multi-stage centrifugal pump with symmetrically configured vane wheel - Google Patents
Dynamic regulation method of axial force in multi-stage centrifugal pump with symmetrically configured vane wheel Download PDFInfo
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- CN1811190A CN1811190A CN 200510041697 CN200510041697A CN1811190A CN 1811190 A CN1811190 A CN 1811190A CN 200510041697 CN200510041697 CN 200510041697 CN 200510041697 A CN200510041697 A CN 200510041697A CN 1811190 A CN1811190 A CN 1811190A
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Abstract
The present invention relates to method of regulating the axial force of multi-stage centrifugal pump and the structure of the multi-stage centrifugal pump, and is especially method of regulating multi-stage centrifugal pump with symmetrically configured front and back vane wheels and in varying axial force. When some axial force increment from the wear of sealing intervals appears in running multi-stage pump, the flow rate of the throttle mechanism in the regulating device is regulated, so that the pressure difference between the outlet and the inlet reaches some preset value, the difference of average pressures inside two specific cavities in the multi-stage pump is controlled in some other preset value and the increment in axial force is counteracted timely and properly to prolong the MTBF and the average life of the pump.
Description
Technical field:
The present invention relates generally to method and multistage centrifugal pump structure thereof that axial force in multi-stage centrifugal pump is regulated and control, relate in particular to multistage centrifugal pump forward and backward two the impeller symmetric arrangement of branch or that near symmetrical is arranged in running when axial force changes to its method of regulating and control.
Background technique:
Axial force is one of principal element that influences the centrifugal pump mean lifetime.In the prior art, for single stage single suction volute pump, the method of balancing axial thrust is to establish seal ring (title increasing back sealing ring) and sealing ring scope is connected with suction port with interior pump chamber on back shroud of impeller, make the pressure basic neutralisation that is born on the forward and backward cover plate of impeller, residual axial force is born by thrust-bearing.Connection method has two kinds: a kind of is to open equalizing orifice in the increasing back sealing ring scope on interior back shroud of impeller, and another kind is with off-load pipe (return pipe) pump chamber in this scope to be connected with suction port.Generally about 10mm, off-load pipe diameter no longer changes its off-load pipe diameter after dispatching from the factory.Multistage centrifugal pump impeller number is at least more than two, tens even more at most.The method of balancing axial thrust has, and A. scroll casing type multistage centrifugal pump has the spirality pumping chamber, and housing is normally opened in the level, adopts impeller symmetric arrangement method to come balancing axial thrust, and residual axial force is born by thrust-bearing; B. to be called the utility model patent of " the multistage slag stock pump of the opposed scroll casing type of sections " disclosed be the multistage slag stock pump of sections scroll casing type to the ZL96217016.X of Shanxi Yangquan City Water Pump Factory name; C. the whole impellers of traditional segmental centrifugal pump are equidirectional to be installed on the pump shaft, and pumping chambers at different levels are stator formula radially, and it is one that stator is strained vertically with turnbuckle.This pump adopts Balance disc or the balancing drum (claiming the off-load dish again) behind the impeller to come balancing axial thrust for a long time always; D. inventor's patent of invention of being called " multistage sectional centrifugal pump of impeller symmetric arrangement " in the ZL02114680.2 name discloses a kind of single suction multistage segmental centrifugal pump, and impeller distributes and is the near symmetrical state, and residual axial force is born by thrust-bearing.The multistage centrifugal pump of above-mentioned various structural types no matter be scroll casing type or stator formula radially, general two classes of dividing of the method for its balancing axial thrust: a class is that the method with symmetric arrangement makes whole pump axial force in a basic balance, bears residual axial force by thrust-bearing; Another kind of is the equidirectional installations of whole impellers, makes the axial force of whole pump reach transient equiliblium with Balance disc, perhaps use the equilibrant of balancing drum (off-load dish) and the axial force of whole pump to reach in a basic balance, and residual axial force is still born by thrust-bearing.The axial force of said pump adjusted before dispatching from the factory is good, no longer regulates and control the work of axial force in running.
But, pump is at run duration, because multistage centrifugal pump often uses under mine or in the open-air field irrigation, the running environment condition is relatively poor, often contain a certain amount of solid particle in the liquid that is pumped, the speed of wearing and tearing is sharply accelerated with the increasing of impurity content and granularity in the pump, and the phase of overhaul first (more than 8000 hours) that causes a large amount of pumps not reach the industry standard regulation far away just damages, the pump that has even can only use hundreds of hours.To the maintenance of disintegrating often of this method that solves in the sector, even renew pump in addition.Unplanned property shutdown phenomenon takes place repeatedly, has had a strong impact on ordinary production.
The inventor is according to for many years observation and research, discovery is along with the prolongation of pump operation time, seal clearance all can strengthen gradually because of wearing and tearing before and after the single suction impeller, the increasing of preceding seal clearance makes pressure distribution that front shroud of impeller bears reduce, the increasing of back seal clearance makes pressure distribution that back shroud of impeller bears raise, and the two causes that all axial force increases so that cause the damage of thrust-bearing along the direction of pointing to single suction impeller water inlet oral-lateral.The traditional single stage single-suction centrifugal pump increases axial force in the said pump running does not have concrete counter-measure, is that this axial force increments of change is less, and pace of change is slower, and the harm that shows is very not serious.And in the actual moving process of multistage pump, all seal clearances all can strengthen gradually because of wearing and tearing, the wearing and tearing of each seal clearance all can cause the outer pressure distribution of two cover plates of every grade of impeller to change, the axial force that every grade of impeller bears is along with increment appears in running, and this axial force incremental raio of most impellers single-stage pump situation is also much bigger in the multistage centrifugal pump.The increment superposition of the axial force that the whole impeller of multistage pump is born shows as the axial force increment that occurs in whole the multistage pump running together.This increment has been compared three distinguishing features with the single-stage pump situation: the one, value is big, the 2nd, change fast, the 3rd, direction and size can be with symmetric arrangement whether with the concrete mode of symmetric arrangement and different.This tends to cause the actual axial force value of whole multistage pump to exceed the axial force excursion of design code, and causes the damage of multistage centrifugal pump.Also be multistage centrifugal pump rate of fault the most basic, the most important reason much higher in the engineering practice far beyond the single stage centrifugal pump rate of fault.The fact is in the prior art, and multistage centrifugal pump is more much higher than the rate of fault that single stage centrifugal pump causes because of axial force is excessive.In a word, the axial force increment that occurs in the running is multistage centrifugal pump causes various faults because of axial force is an excessive root.
Summary of the invention:
The method that the objective of the invention is to avoid the deficiencies in the prior art part and a kind of axial force in multi-stage centrifugal pump of dynamic regulation impeller symmetric arrangement is provided.When the present invention axial force increment occur owing to the wearing and tearing of various seal clearances when multistage pump in running, make the pressure difference at its inlet/outlet two ends reach predetermined value by the throttle mechanism adjusting flow of adjusting in the regulating controller, thereby the difference of the pressure distribution mean value in the control multistage pump in two specific cavitys reaches predetermined value, thereby the axial force increment that occurs because of the seal clearance wearing and tearing in the multistage pump running is carried out timely and appropriate opposite direction to be compensated for, to prolong the mean time between failures (MTBF) of multistage pump, the average life of improving pump.
Purpose of the present invention can be by realizing by the following technical solutions: a kind of method of dynamic regulation axial force in multi-stage centrifugal pump, and its main feature is to include:
A. dividing multistage centrifugal pump forward and backward two symmetric arrangement or that near symmetrical is arranged, its anterior impeller intake points to drive end, anti-drive end is pointed at the rear portion, forwardly impeller (1-3) is provided with increasing back sealing ring (1-9), open regulation and control hole (1-6) on interior cavity (1-4) in increasing back sealing ring (1-9) scope, to regulate and control hole (1-6) with regulating controller (3) and be connected by return port (1-7), perhaps be connected by return port (1-8) with the suction chamber (1-1) of anterior suction side with the suction chamber (1-2) of anterior preceding several grades of impellers.
B. provide the corresponding relation f (P) that changes between the axial force f of increasing back sealing ring (1-9) scope with the pressure P of interior cavity (1-4) and multistage pump, the drive end or the anti-drive end thrust-bearing maximum axial force F allowed to bear that select for use when determining design, and make | f (P) |≤F.
C. use the throttle mechanism (3-1) in the regulating controller (3) to regulate leakage rate in the regulating controller (3), pressure/pressure reduction indicated value P that pressure gauge (3-2) differential pressure meter (3-2 ') is shown as main mechanism for monitoring as the actuator of regulation and control
MinThe thrust-bearing axial force F of selecting for use when reaching design allowed to bear for the residual axial force of multistage centrifugal pump.
D. multistage centrifugal pump brings into operation.
The method of described dynamic regulation axial force in multi-stage centrifugal pump also includes
E. the wearing and tearing that extrude intersegmental axle sleeve position leakage-gap and anterior impeller increasing back sealing ring seal clearance along with front and rear portions in the multistage pump running cause that corresponding leakage rate progressively strengthens, make anterior impeller increasing back sealing ring scope (1-4) internal pressure raise, it is big that the pressure that mechanism for monitoring pressure gauge (3-2) differential pressure meter in the regulating controller (3) (3-2 ') shows/pressure reduction indicated value becomes, by P
MinIncrease gradually and reach P
MaxThe time, repeating the C step, multistage centrifugal pump continues operation.
G. regulate pressure/pressure reduction indicated value P no change that the leakage rate in the regulating controller (3) shows pressure gauge (3-2) differential pressure meter (3-2 ') or change when multistage centrifugal pump runs to throttle mechanism (3-1) in the regulating controller (3-0) at (P
Max-P
MinWhen)/2 were following, the maintenance of disintegrating made after all seal clearances all return to design load and change other flow passage components that worn and torn in the multistage pump, repeats the C step, and multistage centrifugal pump resumes operation.
The method that described dynamic regulation impeller symmetric arrangement gets axial force in multi-stage centrifugal pump also includes in the described A step, the total progression that is multistage pump at multistage centrifugal pump forward and backward two symmetric arrangement of branch or that near symmetrical is arranged is even number, and front and rear portions impeller sum equates; Progression is odd number, and rear portion impeller number is Duoed one than anterior impeller number, on rear portion impeller (2-1) back shroud back blade is housed.
The method of described dynamic regulation axial force in multi-stage centrifugal pump also includes described preceding several grades of impellers and is at least 1 grade.
Also include in the C step of the present invention on the anti-drive end rear bearings body (2-3) of centrifugal pump shaft and be provided with pump axial force testing apparatus (5).
The pump axial force testing apparatus (5) of the method for the axial force in multi-stage centrifugal pump of described dynamic regulation impeller symmetric arrangement is provided with bearing (5-2) at the anti-drive end rear bearings body (2-3) of centrifugal pump shaft, the outer ring of bearing (5-2) is provided with bearing box (5-3), and feather key (5-4) is located between bearing support (4-5) and the bearing box (5-3); Bearing support end cap (5-14) is connected with bearing support (4-5), and its stud end is provided with the shearing force transducer (5-12) that posts foil gauge on spoke; Bearing box gland (5-5) is pressed on bearing (5-2) in the bearing box (5-3) vertically, and its center is fixed with tappet (5-6), passes bearing support end cap (5-14) and is connected with the shearing force transducer of spoke (5-12); Pump axial force testing apparatus (5) is in the stud end of bearing support end cap (5-14) and posting on the spoke between the shearing force transducer (5-12) of foil gauge and be provided with the shearing force transducer (5-15) that posts foil gauge equally on spoke.On pump axial force testing apparatus (5), be provided with the size that the axial force display list can directly show axial force.
The method of the axial force in multi-stage centrifugal pump of described dynamic regulation impeller symmetric arrangement also include described regulation and control hole (1-6) and anterior before the internal diameter of the return port (1-7,1-8) that is connected of the suction chamber (1-1) of the suction chamber (1-2) of several grades of impellers or anterior suction casing be the 1/4-3/4 in multistage centrifugal pump pumping hole footpath.
Described regulating controller includes connecting tube (3-3,3-6), and its two ends are provided with and joining entrance point pipe joint of the pump housing (3-4) and outlet end pipe joint (3-5), also are included in connecting tube (3-3,3-6) and are provided with throttle mechanism (3-1).With the pressure in the throttle mechanism can regulate high-pressure chamber (1-4).
Described regulating controller also included and be provided with mechanism for monitoring pressure gauge (3-2) differential pressure meter (3-2 ') on connecting tube (3-3,3-6).The variation numerical value that can show axial force indirectly.
Described regulating controller also includes connecting tube (3-3) and (3-6), inlet tube interface (3-4) and outlet pipe connection (3-5), flange plate (3-7) are identical with the internal diameter of flange plate (3-8), and are the 1/4-3/4 in multistage pump pumping hole footpath.
Described regulating controller also include throttle mechanism (3-1) for be installed in flange plate (3-7) and (3-8) between the throttling sheet or the restrictor ring (3-9) at least two different apertures.
Described regulating controller also includes described throttle mechanism (3-1) for throttle valve or for the electric throttling valve.
Method of the present invention mainly based on the inventor after to the problems referred to above research as drawing a conclusion:
1. the prolongation of working time, seal clearance all can strengthen gradually because of wearing and tearing before and after the single suction impeller, the increasing of preceding seal clearance makes the pressure distribution that front shroud of impeller bore reduce, and the increasing of inter-stage seal clearance makes the pressure distribution that back shroud of impeller bore raise.The two causes that all axial force increases so that cause the damage of thrust-bearing along the direction of pointing to single suction impeller water inlet oral-lateral.
2. with the pressure in the throttle mechanism can regulate high-pressure chamber (1-4).
Pressure in axial force and the cavity (1-4) or cavity (1-4) and anterior impeller before between the suction chamber of impeller or the anterior suction chamber pressure difference have more definite one-to-one relationship.
The invention has the beneficial effects as follows:
1. simple in structure, reasonable in design.
2. the axial force increment that occurs in coming pump operation of the actuator that adjusts regulating controller by the user of pump in the pump operation process carries out timely and appropriate opposite direction and compensates for, and whether the reverse setoff work of directly or indirectly being monitored actuator by the mechanism for monitoring of regulating controller is appropriately reasonable.Saving of work and time, convenient and swift, can prevent unplanned property shutdown phenomenon, thereby multistage centrifugal pump mean time between failures (MTBF) and average life are greatly prolonged that the reliability index of pump is doubled and redoubled, and makes its regulation of industry standard head and shoulders above.Owing to flexible and suitable adjustment etc. that total progression i, impeller arrangement and other flow passage components of pump are made comparisons, the efficient of multistage centrifugal pump is increased simultaneously.
3. the mechanism for monitoring of the actuator of regulating controller and the regulating controller position very obviously and easily, outside that is installed in the pump housing is convenient to the axial force in multi-stage centrifugal pump increment is carried out timely and appropriate setoff.
4. be applicable to scroll casing type or stator formula, the multistage centrifugal pump of structural type such as horizontal or vertical.
Description of drawings:
Be described in further detail below in conjunction with the most preferred embodiment shown in the accompanying drawing:
Fig. 1 is Application Example 1 plan view of the present invention.
Fig. 2 is Application Example 2 plan views of the present invention.
Fig. 3 looks schematic representation for pump axial force testing apparatus master of the present invention.
Fig. 4 is regulating controller embodiment's 1 an of the present invention plan view.
Fig. 5 is regulating controller embodiment's 2 an of the present invention plan view.
Embodiment:
Application examples: see Fig. 1, be six grades of centrifugal pumps of single suction of the impeller symmetric arrangement of model MDZ85-67X6, whole pump is divided into two groups of front and rears, and 1 is the front portion structure of pump, and 2 is the rear structure of pump, and anterior impeller is opposite with rear portion impeller inlet direction.Total progression of multistage pump is even number, and front and rear portions impeller sum equates.Above general arrangement mode can make forward and backward two groups of big portions of the axial force that impeller bore cancel each other.Dividing multistage centrifugal pump forward and backward two symmetric arrangement or that near symmetrical is arranged, its anterior impeller intake points to drive end, anti-drive end is pointed at the rear portion, forwardly take turns 1-3 last years of a century and be provided with increasing back sealing ring 1-9, the suction chamber 1-2 of several grades of impellers or the suction chamber 1-1 of anterior suction casing are connected by return port 1-7,1-8 before increasing back sealing ring 1-9 scope is opened regulation and control hole 1-6 on interior cavity 1-4 will regulate and control hole 1-6 and front portion with regulating controller 3.Regulation and control hole 1-6 is connected with the inlet connector tube 3-4 of regulating controller 3, and the outlet pipe connection 3-5 of regulating controller 3 is connected with the suction chamber 1-1 of anterior stage casing 1-2 or anterior suction casing.The main liquid stream of carrying liquid by being connected with the suction chamber 2-2 of rear portion suction casing with the isodiametric pipeline of pump inlet/outlet, extrudes from the Spit Section, rear portion after the extrusion of anterior Spit Section at last.Rear bearings body 2-3 goes up pairing angular contact ball bearing 2-4 is installed.
Whole pump factory before, by actual measurement provide regulation and control axial force monitor value:
| Pump discharge pressure (MPa) | 4.58 | 4.50 | 4.37 | 4.20 | 3.98 | 3.72 | 3.53 | 3.32 | |
| Flow (m 3/h) | 45 | 55 | 65 | 75 | 85 | 95 | 102 | 110 | |
| Mechanism for monitoring pressure (MPa) | Initial value | 1.56 | 1.52 | 1.47 | 1.41 | 1.34 | 1.26 | 1.19 | 1.11 |
| Control value | 2.08 | 2.04 | 1.97 | 1.93 | 1.86 | 1.78 | 1.71 | 1.63 | |
The throttling sheet 3-9 of the aperture minimum of regulating controller throttle orifice being installed, making the residual axial force of whole multistage pump reach the initial value of mechanism for monitoring pressure, is 3.98MPa as pump discharge pressure, and flow is 85m
3/ h, the initial value of its mechanism for monitoring pressure is 1.34MPa, along with the wearing and tearing axial force of seal clearance in the multistage pump running will change, but because before the multistage pump of this kind structural type is in operation, the reason of the relevant seal clearance symmetry of the most impellers in rear portion wearing and tearing, pressure in operating actual axial force and the cavity 1-4 or and cavity 1-4 and anterior impeller the suction chamber of impeller or the pressure difference between the anterior suction chamber have more definite one-to-one relationship before, along with preceding, the wearing and tearing of axle sleeve position leakage-gap and anterior impeller increasing back sealing ring seal clearance cause that corresponding leakage rate progressively strengthens between the Spit Section, rear portion, make the cavity 1-4 internal pressure of anterior impeller increasing back sealing ring scope raise, it is big that thereby the show value of pressure gauge 3-2 differential pressure meter 3-2 ' becomes, and the residual axial force of whole multistage pump is by-f
mBeginning is little by little become zero and then is become forward by negative.The forward maximum permissible value f of residual axial force
mNegative sense axial force-f during with beginning
mAbsolute value equates, selects the maximum value of the axial force that doubledirection thrust bearing allows when also equaling to design for use, reaches control value 2.08MPa when residual axial force reaches mechanism for monitoring pressure.By the user throttling sheet 3-9 is replaced by the bigger throttling sheet 3-9 in aperture again, makes the variation of axial force repeat above-mentioned " f
m-null value-f
m" change procedure, corresponding pressure gauge 3-2 show value repeats above-mentioned 1.56MPa-2.08MPa differential pressure meter 3-2 ' and repeats above-mentioned " Δ P
Min-Δ P
Max" change procedure.Change procedure of every experience just is replaced by throttling sheet 3-9 the bigger throttling sheet 3-9 in aperture, until all standby 5 throttling sheet 3-9 are exhausted, pump is overhauled again.Change cycle and the clean degree (impurity content and granularity thereof) of institute's pumping liquid, material that various seal clearance uses and some other specific design relating to parameters of a throttling sheet 3-9.
As long as the show value of pressure gauge 3-2 differential pressure meter 3-2 ' is in the scope of regulation, then residual axial force also just is in-f
m, f
mBetween.Residual axial force is with the changes in flow rate of pump, therefore thisly will provide " regulating controller pressure gauge reading minimum P when pumping factory
Min, maximum P
Max-inlet/outlet pressure (flow) " curve or provide " differential pressure gauge reading minimum Δ P
Min, maximum Δ P
Max-inlet/outlet pressure (flow) " curve, this curve also should be adjusted by the actual suction vacuum that the back pump is installed, so that be in operation the situation of change of indirect monitoring axial force at any time.
Application examples 2: Fig. 2, but the multistage centrifugal pump of the impeller symmetric arrangement of dynamic regulation axial force are provided with pump axial force testing apparatus 5 on the anti-drive end rear bearings body 2-3 of centrifugal pump shaft.On pump axial force testing apparatus 5, be provided with the size that the axial force display list can directly show axial force.The structure of pump axial force testing apparatus 5 is reported patent in addition.
Fig. 3, pump axial force testing apparatus 5 is provided with bearing 5-2 at the anti-drive end rear bearings body 2-3 of centrifugal pump shaft, and the outer ring of bearing 5-2 is provided with bearing box 5-3, and feather key 5-4 is located between bearing support 2-3 and the bearing box 5-3; Bearing support end cap 5-14 and bearing support 2-3 are connected, and its stud end is provided with the shearing force transducer 5-12 that posts foil gauge on spoke; Bearing box gland 5-5 is pressed on bearing 5-2 in the bearing box 5-3 vertically, and its center is fixed with tappet 5-6, passes the shearing force transducer 5-12 of bearing support end cap 5-14 and spoke and is connected.In the stud end of bearing support end cap 5-14 and posting on the spoke between the shearing force transducer 5-12 of foil gauge and also be provided with the shearing force transducer 5-15 that on spoke, posts foil gauge equally.
Regulating controller embodiment 1: see Fig. 4, connecting tube 3-3,3-6 are arranged, its two ends are provided with and the pump housing joining entrance point pipe joint 3-4 and outlet end pipe joint 3-5, are provided with throttle mechanism 3-1 on connecting tube 3-3,3-6.On connecting tube 3-3,3-6, also be provided with mechanism for monitoring pressure gauge 3-2.The caliber of connecting tube 3-3,3-6 is 1/2 of multistage pump pumping hole footpath.Throttle mechanism 3-1 is provided with the restrictor ring 3-9 in six different mesopores apertures for be provided with flange plate 3-7,3-8 on connecting tube 3-3,3-6 between two dishes.
Regulating controller embodiment 2: see Fig. 5, throttle mechanism 3-1 is throttle valve or is the electric throttling valve.All the other structures are identical with last example.
Claims (10)
1. the method for the axial force in multi-stage centrifugal pump of a dynamic regulation impeller symmetric arrangement is characterized in that including:
A. dividing multistage centrifugal pump forward and backward two symmetric arrangement or that near symmetrical is arranged, its anterior impeller intake points to drive end, anti-drive end is pointed at the rear portion, forwardly impeller (1-3) is provided with increasing back sealing ring (1-9), open regulation and control hole (1-6) on interior cavity (1-4) in increasing back sealing ring (1-9) scope, to regulate and control hole (1-6) with regulating controller (3) and be connected by return port (1-7), perhaps be connected by return port (1-8) with the suction chamber (1-1) of anterior suction casing with the suction chamber (1-2) of anterior preceding several grades of impellers.
B. provide the corresponding relation f (P) that changes between the axial force F of increasing back sealing ring (1-9) scope with the pressure P of interior cavity (1-4) and multistage pump, the drive end or the anti-drive end thrust-bearing maximum axial force F allowed to bear that select for use when determining design, and make | f (P) |≤F.
C. use the throttle mechanism (3-1) in the regulating controller (3) to regulate leakage rate in the regulating controller (3), pressure/pressure reduction indicated value P that pressure gauge (3-2) differential pressure meter (3-2 ') is shown as main mechanism for monitoring as the actuator of regulation and control
MinThe anti-drive end thrust-bearing axial force F of selecting for use when reaching design allowed to bear for the residual axial force of multistage centrifugal pump.
D. multistage centrifugal pump brings into operation.
2. the method for the axial force in multi-stage centrifugal pump of dynamic regulation impeller symmetric arrangement as claimed in claim 1 is characterized in that also including
E. the wearing and tearing that extrude intersegmental axle sleeve position leakage-gap and anterior impeller increasing back sealing ring seal clearance along with front and rear portions in the multistage pump running cause that corresponding leakage rate progressively strengthens, make anterior impeller increasing back sealing ring scope (1-4) internal pressure raise, it is big that the pressure that mechanism for monitoring pressure gauge (3-2) differential pressure meter in the regulating controller (3) (3-2 ') shows/pressure reduction indicated value becomes, by P
MinIncrease gradually and reach P
MaxThe time, repeating the C step, multistage centrifugal pump continues operation.
F. regulate pressure/pressure reduction indicated value P no change that the leakage rate in the regulating controller (3) shows pressure gauge (3-2) differential pressure meter (3-2 ') or change when multistage centrifugal pump runs to throttle mechanism (3-1) in the regulating controller (3) at (P
Max-P
MinWhen)/2 were following, the maintenance of disintegrating made after all seal clearances all return to design load and change other flow passage components that worn and torn in the multistage pump, repeats the C step, and multistage centrifugal pump resumes operation.
3. the method for the axial force in multi-stage centrifugal pump of dynamic regulation impeller symmetric arrangement as claimed in claim 1 or 2, it is characterized in that also including in the described A step, the total progression that is multistage pump at multistage centrifugal pump forward and backward two symmetric arrangement of branch or that near symmetrical is arranged is even number, and front and rear portions impeller sum equates; Progression is odd number, and rear portion impeller number is Duoed one than anterior impeller number, on rear portion impeller (2-1) back shroud back blade is housed.
4. the method for the axial force in multi-stage centrifugal pump of dynamic regulation impeller symmetric arrangement as claimed in claim 1 or 2 is characterized in that also including also including in the described C step on the anti-drive end rear bearings body (2-3) of centrifugal pump shaft and is provided with pump axial force testing apparatus (5).
5. the method for the axial force in multi-stage centrifugal pump of dynamic regulation impeller symmetric arrangement as claimed in claim 4, it is characterized in that described pump axial force testing apparatus (5) is provided with bearing (5-2) at the anti-drive end rear bearings body (2-3) of centrifugal pump shaft, the outer ring of bearing (5-2) is provided with bearing box (5-3), and feather key (5-4) is located between bearing support (4-5) and the bearing box (5-3); Bearing support end cap (5-14) is connected with bearing support (4-5), and its stud end is provided with the shearing force transducer (5-12) that posts foil gauge on spoke; Bearing box gland (5-5) is pressed on bearing (5-2) in the bearing box (5-3) vertically, and its center is fixed with tappet (5-6), passes bearing support end cap (5-14) and is connected with the shearing force transducer of spoke (5-12); Pump axial force testing apparatus (5) is in the stud end of bearing support end cap (5-14) and posting on the spoke between the shearing force transducer (5-12) of foil gauge and be provided with the shearing force transducer (5-15) that posts foil gauge equally on spoke.
6. the method for the axial force in multi-stage centrifugal pump of dynamic regulation impeller symmetric arrangement as claimed in claim 1 is characterized in that also including described preceding several grades of impellers and is at least 1 grade.
7. the axial force in multi-stage centrifugal pump method of dynamic regulation impeller symmetric arrangement as claimed in claim 1, it is characterized in that described regulating controller includes connecting tube (3-3,3-6), its two ends are provided with and joining entrance point pipe joint of the pump housing (3-4) and outlet end pipe joint (3-5), are provided with throttle mechanism (3-1) on connecting tube (3-3,3-6).
8. as the axial force in multi-stage centrifugal pump method of dynamic regulation impeller symmetric arrangement as described in the claim 7, it is characterized in that described regulating controller also includes on connecting tube (3-3,3-6), to be provided with mechanism for monitoring pressure gauge (3-2) differential pressure meter (3-2 ').
9. as the axial force in multi-stage centrifugal pump method of dynamic regulation impeller symmetric arrangement as described in claim 1 or 7, it is characterized in that described regulating controller also include described regulation and control hole (1-6) and anterior before the internal diameter of the return port (1-7,1-8) that is connected of the suction chamber (1-1) of the suction chamber (1-2) of several grades of impellers or anterior suction casing be the 1/4-3/4 in multistage centrifugal pump pumping hole footpath; The internal diameter of connecting tube (3-3,3-6), inlet connector tube (3-4) and outlet pipe connection (3-5), flange plate (3-7) and flange plate (3-8) is the 1/4-3/4 in multistage pump pumping hole footpath.
10. as the axial force in multi-stage centrifugal pump method of dynamic regulation impeller symmetric arrangement as described in the claim 6, it is characterized in that described regulating controller also include throttle mechanism (3-1) for the throttling sheet that is provided with two different apertures between flange plate (3-7) and the flange plate (3-8) at least or restrictor ring (3-9) or throttle mechanism (3-1) for throttle valve or be the electric throttling valve.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100416978A CN100455815C (en) | 2005-01-30 | 2005-01-30 | Dynamic regulation method of axial force in multi-stage centrifugal pump with symmetrically configured vane wheel |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100416978A CN100455815C (en) | 2005-01-30 | 2005-01-30 | Dynamic regulation method of axial force in multi-stage centrifugal pump with symmetrically configured vane wheel |
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| CN1811190A true CN1811190A (en) | 2006-08-02 |
| CN100455815C CN100455815C (en) | 2009-01-28 |
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| CNB2005100416978A Expired - Fee Related CN100455815C (en) | 2005-01-30 | 2005-01-30 | Dynamic regulation method of axial force in multi-stage centrifugal pump with symmetrically configured vane wheel |
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| CN (1) | CN100455815C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102182695A (en) * | 2011-05-23 | 2011-09-14 | 新乡泵厂有限责任公司 | Tester for axial force of pump |
| CN102734176A (en) * | 2011-03-29 | 2012-10-17 | 格伦德福斯管理联合股份公司 | Multi stage centrifugal pump system |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5847171A (en) * | 1981-09-14 | 1983-03-18 | Toshiba Corp | Multi-stage hydraulic machinery |
| CN2129820Y (en) * | 1992-07-08 | 1993-04-14 | 石油管理局川中矿区 | Lens flow controller |
| CN1144954C (en) * | 2001-04-09 | 2004-04-07 | 哈尔滨工程大学 | Magnetically driven pump |
| CN1439809A (en) * | 2002-07-10 | 2003-09-03 | 甘肃工业大学 | Multistage segmental centrifugal pump |
-
2005
- 2005-01-30 CN CNB2005100416978A patent/CN100455815C/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102734176A (en) * | 2011-03-29 | 2012-10-17 | 格伦德福斯管理联合股份公司 | Multi stage centrifugal pump system |
| CN110307166A (en) * | 2011-03-29 | 2019-10-08 | 格伦德福斯管理联合股份公司 | Multistage centrifugal pump assembly |
| EP2505842B1 (en) | 2011-03-29 | 2019-12-25 | Grundfos Management a/s | Multi stage centrifugal pump system |
| CN102182695A (en) * | 2011-05-23 | 2011-09-14 | 新乡泵厂有限责任公司 | Tester for axial force of pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100455815C (en) | 2009-01-28 |
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