CN1232928A - Thrust balance device - Google Patents
Thrust balance device Download PDFInfo
- Publication number
- CN1232928A CN1232928A CN99105578A CN99105578A CN1232928A CN 1232928 A CN1232928 A CN 1232928A CN 99105578 A CN99105578 A CN 99105578A CN 99105578 A CN99105578 A CN 99105578A CN 1232928 A CN1232928 A CN 1232928A
- Authority
- CN
- China
- Prior art keywords
- aforementioned
- thrust
- impeller
- protuberance
- cylindrical body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; 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
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2261—Rotors specially for centrifugal pumps with special measures
- F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance
-
- 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
- F04D29/0416—Axial thrust balancing balancing pistons
Abstract
The invention provides a thrust balance apparatus of good thrust balance properties. The thrust balance apparatus is constructed by disposing on the liner disk a ring shaped groove communication with the thrust balance chamber and equalizing portion.
Description
The invention relates to the invention of thrust balancing device, more particularly, is the invention about the thrust balancing device that can increase substantially the thrust-balancing characteristic that for example shields motor-drive pump.
Existing shielding motor-drive pump has running shaft and is contained in impeller on this running shaft.In this shielding motor-drive pump, from the fluid that the suction port to running shaft direction opening sucks, be subjected to the action of centrifugal force of rotary blade, discharge from exhaust port to the radial direction opening.Because suction port is to running shaft direction opening, so impeller is subjected to the effect of power in thrust direction.Like this, the impeller of original shielding motor-drive pump can be pushed to the casing inner wall of adorning impeller, causes obstacle for the rotation of impeller.Therefore, nearly all in recent years shielding motor-drive pump all is equipped with thrust balancing device at suitable position.
This thrust balancing device is the device that a kind of pressure that prevents the thrust direction that produced by the fluid that sucks hinders the impeller rotation.Usually, this device has
(1) the ring-type cylindrical body that will be formed at the impeller the inside with equalizing orifice inserts and is arranged at depressed part on the casing, that have the cylindrical shape inner peripheral surface, the fixed orifice that forms by the gap between the cylindrical shape inner peripheral surface of the outer circumferential face of aforementioned cylindrical body and aforementioned depressed part
(2) by the bottom surface of aforementioned cylindrical body, the inner peripheral surface of this cylindrical body, the inner space of contiguous aforementioned cylindrical body, on casing outstanding the 1st protuberance that forms towards aforementioned bottom surface and the face of certain intervals arranged with it, and thrust-balancing chamber more outstanding more than aforementioned the 1st protuberance, that constitute around the outer circumferential face of ring-type the 2nd protuberance of running shaft, and
(3) aforementioned the 2nd protuberance is towards the front-end face of impeller the inside and the variable orifice of impeller the inside formation.
In this thrust balancing device because the rotation of impeller produces centrifugal force fluid is radially discharged, but the fluid that centrifugal direction is discharged some flow into the thrust-balancing chamber by the aforementioned fixation throttle orifice.Flow into the fluid of thrust-balancing chamber, it is outdoor to flow to thrust-balancing by variable orifice, and the fluid that flows out from the thrust-balancing chamber collaborates by the fluid of equalizing orifice and discharge.
If the hydrodynamic pressure that sucks, discharges raises, impeller is subjected to the pressure of thrust direction, and the inside of impeller will be near the casing face towards this inside.But, because the pressure of fluid, by the fluid flow increase of fixed orifice, the indoor hydrodynamic pressure of thrust-balancing just increases, so, because the indoor hydrodynamic pressure of thrust-balancing increases, impeller just is under pressure, and makes impeller leave casing towards this inside.This pressure also claims self-support power.Because the indoor hydrodynamic pressure of this thrust-balancing, impeller overcome the pressure of suction, discharge fluid and move.
Like this, impeller one leaves towards the casing of its inside and moves, in other words is exactly that impeller one leaves towards the casing face of this inside and the mobile position, and the gap of variable orifice is with regard to increase, and the fluid of increased pressure flows out rapidly from this variable orifice.Consequently the indoor pressure of thrust-balancing descends, and the fluid that sucks, discharges imposes on the pressure of thrust direction of impeller greater than the indoor hydrodynamic pressure of thrust-balancing.Impeller is subjected to the pressure of thrust direction, and move towards the casing face of impeller the inside its position.
As mentioned above, impeller can be shifted one's position according to the gap of fixed orifice, the gap of variable orifice and the volume of thrust-balancing chamber, the pressure of indoor pressure of thrust-balancing and suction, discharge fluid is averaged out, thereby running shaft is averaged out on thrust direction.
But, having the thrust balancing device of this existing structure, in its thrust-balancing chamber, the impeller the inside is a surface of revolution, is stationary plane towards the casing face of this impeller.Therefore, the fluid that flows into this thrust-balancing chamber will be subjected to the angular kinetic energy that produces because of the impeller rotation, rotates with the rotation of impeller.Indoor at thrust-balancing, to rotate the fluid passage impedance that produces with impeller very big because of fluid.
The fluid passage impedance of the fluid of surface of revolution between stationary plane and the linear velocity of the fluid that rotates with surface of revolution square are directly proportional.Therefore, in the great high speed pump of wheel speed, even if perhaps be not high speed pump, but the amount of fluid is big in the gap between stationary plane and the surface of revolution, in the very big magna pump of the linear velocity of fluid of rotation, the fluid passage impedance of the fluid that thrust-balancing is indoor is very big, and thrust-balancing just is difficult to suitably keep.
In order to address this problem, the someone has adopted the tap hole that is called as balancing orifice or vent has been set on the stationary plane of thrust-balancing chamber, but this does not reach the impedance of reduction fluid passage, suitably keeps the purpose of balance.Why saying so, is because aforesaid tap hole is set, though can increase self-support power, can not reduce the angular kinetic energy of the indoor fluid of thrust-balancing significantly.
The thrust balancing device that the purpose of this invention is to provide a kind of thrust-balancing function admirable.
Even it is very big to the purpose of this invention is to provide a kind of discharge capacity of pump, the thrust balancing device that the thrust-balancing performance is also still good.
Even the purpose of this invention is to provide a kind of pump with high-speed rotating impeller, the thrust balancing device that its thrust-balancing performance is also still good.
Thrust balancing device of the present invention has
(1) will be formed at the ring-type cylindrical body that has equalizing orifice and be contained in the impeller the inside on the running shaft inserts and is arranged at depressed part on the casing, that have the cylindrical shape inner peripheral surface, the fixed orifice that forms by the gap between the cylindrical shape inner peripheral surface of the outer circumferential face of aforementioned cylindrical body and aforementioned depressed part
(2) by the bottom surface of aforementioned cylindrical body, the inner peripheral surface of this cylindrical body, the inner space of contiguous aforementioned cylindrical body, on casing outstanding the 1st protuberance that forms towards aforementioned bottom surface and the face of certain intervals arranged with it, and thrust-balancing chamber more outstanding more than aforementioned the 1st protuberance, that constitute around the outer circumferential face of ring-type the 2nd protuberance of running shaft
(3) aforementioned the 2nd protuberance is towards the front-end face of impeller the inside and the variable orifice of impeller the inside formation,
(4) on aforementioned the 1st protuberance, form, around the annular groove of aforementioned running shaft, and
(5) the equal splenium of aforementioned annular groove of connection and aforementioned depressed part.
The preferred embodiment of aforementioned thrust balancing device is that the opening area of the sectional area summation of the axis normal direction of described equal splenium and aforementioned the 1st protuberance of described annular groove is greater than the thrust balancing device of the summation of aforementioned equalizing orifice opening area.
The present invention is described with reference to the accompanying drawings.
Fig. 1 is the longitudinal section of an example of expression the present invention.
Fig. 2 is the longitudinal section of another example of expression the present invention.
Fig. 3 is the longitudinal section of another example of expression the present invention.
Fig. 4 is the longitudinal section of another example of expression the present invention.
Fig. 5 is a kind of shielding motor-drive pump of expression, the centrifugal pump that promptly has thrust balancing device shown in Figure 1, and except not having aforementioned thrust balancing device, all the other all identical shielding motor-drive pumps with aforementioned shielding motor-drive pump when discharge flow rate changes, the plotted curve that residual thrust changes.
Example 1
This example 1 is an example of thrust balancing device of the present invention.
Fig. 1 be the expression thrust balancing device of adorning example 1 centrifugal pump partly cut open sectional view.
As shown in Figure 1, adorning the centrifugal pump 1 of the thrust balancing device of the present invention's one example, having casing 2 and support 3, in the pump chamber 4 that this casing 2 and support 3 form, the impeller 6 that is contained on the running shaft 5 is being arranged.
The suction port of this centrifugal pump 1 is not expressed in Fig. 1, and it is formed at towards the axial position of impeller 6.Its axis cylindric guiding road 7 identical with the axis of running shaft 5 arranged from this suction port to pump chamber till 4.
In thrust balancing device of the present invention,, promptly on the side of support 3, be formed with the cylindrical body of giving prominence to support 39 in the inside of the aforementioned substrates 8 that constitutes impeller 6 parts.On this matrix 8, also offer the impeller bore 10 that always is through to guiding road 7 one side surfaces from the inside near the matrix 8 of running shaft 5.
, on the face of aforementioned substrates 8, formed and had the depressed part 11 that internal diameter is slightly larger than the cylindrical shape inner peripheral surface of aforementioned cylindrical body 9 diameters at support 3.Aforementioned cylindrical body 9 inserts this depressed part 11.Form a very little gap between the outer circumferential face of the cylindrical body 9 that inserts and the inner peripheral surface of this depressed part 11.This gap promptly is a fixed orifice 12.
In aforementioned depressed part 11, inboard at aforementioned cylindrical body 9, be formed with towards outstanding discoid the 1st protuberance 13 of impeller 6 inboard faces, inboard at the 1st protuberance 13, near running shaft 5, be formed with than the more approaching aforementioned impeller 6 inboard faces of aforementioned the 1st protuberance 13, the 2nd protuberance 14 with annular end face.The end face towards aforementioned cylindrical body 9 bottom surfaces of the 1st protuberance 13 is a ring-type.Insert under the situation of this depressed part 11 at aforementioned cylindrical body 9, form certain clearance between the inner peripheral surface of the outer circumferential face of the 1st protuberance 13 and cylindrical body 9.This gap is set at more many greatly than aforementioned fixation throttle orifice 12.The annular end face of the 2nd protuberance 14 is from axially looking in the form of a ring.
Thrust-balancing chamber 15 is formed with determined space, the bottom surface (this face is the inside of impeller, is surface of revolution) of aforementioned cylindrical body 9 by the annular end face (this face also is a stationary plane) of the 1st protuberance 13.
The annular end face of the 2nd protuberance 14 and the bottom surface of cylindrical body are that the gap between the inside of matrix 8 is exactly a variable orifice 16.
Being formed with running shaft 5 by the 2nd protuberance 14 places at aforementioned the 1st protuberance 13 is the annular groove 17 at center.This annular groove 17 has the opening portion by the annular end face that is opened on the 1st protuberance 13, with the axis identical with the axis of running shaft 5 be the cylindrical body 9 at center outer circumferential face, be inboard inner peripheral surface, and with the axis identical with the axis of running shaft 5 be the inner peripheral surface of the cylindrical body 9 at center, promptly the outside inner peripheral surface around the ditch space.This ditch space is that running shaft 5 is the annulus at center.In Fig. 1 of longitudinal section, the longitudinal section ora terminalis line of inboard inner peripheral surface is parallel with the longitudinal section ora terminalis line of outside inner peripheral surface.
All splenium 18 is formed by the penetration hole that the outer circumferential face from aforementioned the 1st protuberance 13 runs through aforementioned annular groove 17.This equal splenium 18 is communicated with aforementioned annular groove 17 and depressed part 11.This penetration hole, be that equal splenium 18 is provided with 12 on the 1st protuberance 13.This equal splenium with the axis normal direction on the cross section be circular, therefore, this equal splenium has columnar inner space.
Effect with thrust balancing device describes to centrifugal pump 1 with above structure below.
Running shaft 5 one rotary blades 6 i.e. rotation thereupon.The fluid of introducing from suction port flows into pump chamber 4 through guiding road 7.In pump chamber 4, because of the rotation of impeller 6, its centrifugal force makes fluid discharge from exhaust port.This is the effect of common centrifugal pump 1.
A part of fluid in the pump chamber 4 flows into thrust-balancing chamber 15 by aforesaid fixed orifice 12, by variable orifice 16, passes the surface that equalizing orifice 10 is got back to impeller 6.
If the head pressure of impeller 6 one sides increases, impeller 6 because of this head pressure near support 3 one side shiftings.Like this, the gap of variable orifice 16 is narrower and small than originally.The flow of the fluid that flows out from this variable orifice 16 reduces.On the other hand, though the gap stenosis of variable orifice 16 is little, the gap of fixed orifice 12 but still there is not change, so fluid continues to flow in the thrust-balancing chamber 15.In in fluid continues to flow into thrust-balancing chamber 15, the gap of variable orifice 16 is compared original narrow and smallly because of increasing of head pressure, and therefore the fluid flow that flows out from variable orifice 16 is restricted.Consequently the hydrodynamic pressure in the thrust-balancing chamber 15 increases.Then the hydrodynamic pressure that is thrust-balancing chamber 15 is higher than head pressure.
In a single day the hydrodynamic pressure of thrust-balancing chamber 15 is higher than head pressure, and impeller 6 just moves to the direction that cylindrical body 9 is extracted from depressed part 11.The mobile gap enlargement that makes variable orifice 16 of impeller 6.The gap enlargement of variable orifice 16, the flow that fluid in the thrust-balancing chamber 15 flows out from variable orifice 16 becomes many, Fluid Volume in the thrust-balancing chamber 15 reduces, and consequently the hydrodynamic pressure in the thrust-balancing chamber 15 becomes consistent with the head pressure of impeller 6 one sides, and impeller 6 stops to move.
But the fluid itself that is present in the thrust-balancing chamber 15 rotates along with the rotation of impeller 6.The fluid of rotation has moment of momentum in thrust-balancing chamber 15, can produce the fluid passage impedance.This fluid passage impedance is as increasing, even if the gap enlargement of variable orifice 16, the fluid in the thrust-balancing chamber 15 also is difficult to promptly flow out from variable orifice 16.
The objective of the invention is to reduce the fluid passage impedance that the moment of momentum because of fluid produces.Therefore, in this example of the present invention, be provided with annular groove 17 and equal splenium 18.There is not the fluid of moment of momentum to flow in the thrust-balancing chamber 15 through annular groove 17 by allowing from this equal splenium 18, mix with fluid with moment of momentum, the moment of momentum of the fluid in the thrust-balancing chamber 15 is reduced rapidly, allow in the thrust-balancing chamber 15 fluid rapidly, waltz through variable orifice 16 and flow out.
With computer to having the pump of equal splenium 18 and annular groove 17, and the thrust-balancing of the running shaft 5 of the pump that has only equal splenium 18 is carried out Simulation result show, the fluid discharge of having only the variable orifice 16 of the pump of equal splenium 18 to flow out is 290 liters/minute, the hydrodynamic pressure at impeller 6 back sides (pressure in the thrust-balancing chamber 15) is 2363N (241kgf), having the fluid discharge that the variable orifice 16 of equal splenium 18 and the pump of annular groove 17 flows out is 301 liters/minute, the hydrodynamic pressure at impeller 6 back sides is 2157N (220kgf), and tangible minimizing is arranged.The pump size that adopts when calculating is SUC125A, DIS100A, 200m
3/ h * 32m * 2900rpm, impeller diameter are Φ 190.
The modified example of example 1
In structure of the present invention, annular groove 17 is as long as form on aforementioned the 1st protuberance 13, and around aforementioned running shaft 5, Qi Gou in any case can in the space.For example, as shown in Figure 2, annular groove 17 can be the opening portion that has by the annular end face that is opened on the 1st protuberance 13, being equivalent to the axis identical with the axis of running shaft 5 is the inboard inner peripheral surface of cylindrical body 9 outer circumferential faces at center, and be equivalent to the axis identical with the axis of running shaft 5 be the center the cone inner peripheral surface outside inner peripheral surface around the ditch space.In this case, in longitudinal section shown in Figure 2, the longitudinal section in this ditch space is wedge type.Another example of annular groove 17 is the opening portion that has by the annular end face that is opened on the 1st protuberance 13, being equivalent to the axis identical with the axis of running shaft 5 is the inboard inner peripheral surface of the cone outer circumferential face at center, and be equivalent to the axis identical with the axis of running shaft 5 be the center cylindrical body 9 inner peripheral surfaces outside inner peripheral surface around the ditch space.In this case, in longitudinal section shown in Figure 3, the longitudinal section in this ditch space is wedge type.Another example of annular groove 17 is the opening portion that has by the annular end face that is opened on the 1st protuberance 13, being equivalent to the axis identical with the axis of running shaft 5 is the inboard inner peripheral surface of the cone outer circumferential face at center, and be equivalent to the axis identical with the axis of running shaft 5 be the center the cone inner peripheral surface outside inner peripheral surface around the ditch space.
No matter the ditch space of annular groove 17 is any shape, and all (A is with n * (π/4) * d for the splenium 18 summation A long-pending with the circular cross-section of axis normal direction
1 2Calculate, wherein n represents the number of equal splenium 18) basically, preferably be less than opening area B (B (π/4) * (D of annular groove 17
2 2-D
3 2) calculate) (be A＜B).
Among the summation A of the aforementioned circle sectional area of aforementioned equal splenium 18 and the opening area B of aforementioned annular groove 17 any one all than equalizing orifice 10 at the big thrust balancing device of the opening area summation of matrix 8, because of its thrust-balancing performance is good especially, so more satisfactory.
All the number of splenium 18 has no particular limits.
Embodiment 1
In shielding motor-drive pump (model: the thrust balancing device with structure shown in Figure 1 is set HN25E), allows discharge flow rate at 10～140m
3Change in the scope of/h, measure hydrodynamic pressure in the thrust-balancing chamber 15 and impeller 6 one sides head pressure poor, be residual thrust.
In the thrust balancing device of aforementioned shielding motor-drive pump, among the summation A of the aforementioned circle sectional area of aforementioned equal splenium 18 and the opening area B of aforementioned annular groove 17 any one is all big in the opening area summation of matrix 8 than equalizing orifice 10, and all the summation A of the aforementioned circle sectional area of splenium 18 is littler than the aforementioned opening area B of annular groove 17.Aforementioned shielding motor-drive pump drives with the Ac of 50Hz.Measurement result as shown in Figure 5.
As shown in Figure 5, the discharge flow rate of aforementioned shielding motor-drive pump is at 10～140m
3In the time of in the scope of/h, residual thrust is almost nil, and the hydrodynamic pressure in the thrust-balancing chamber 15 and the head pressure of impeller 6 one sides are roughly coincide.Wherein,
The curve that to be the used shielding motor-drive pump flow of expression embodiment 1 concern with residual thrust.
Comparative example 1
Except not having annular groove 17 and equal splenium 18, the shielding motor-drive pump that all the other structures are all identical with embodiment 1 (model: HN25E-F4), under the condition identical, in identical discharge flow rate scope with embodiment 1, measure its residual thrust, the result as shown in Figure 5.
As shown in Figure 5, aforementioned shielding motor-drive pump has produced the residual thrust to about the up 70kgf of impeller 6 directions from thrust-balancing chamber 15.Wherein,
The curve that to be the used shielding motor-drive pump flow of expression comparative example 1 concern with residual thrust.
The present invention can provide a kind of thrust balancing device of thrust-balancing function admirable.
Even the present invention can provide a kind of discharge capacity of pump very big, the thrust balancing device that the thrust-balancing performance is also still good.
Even the present invention can provide a kind of pump with high-speed rotating impeller, the thrust balancing device that its thrust-balancing performance is also still good.
Claims (2)
1. a thrust balancing device is characterized in that having
The ring-type cylindrical body that has equalizing orifice with being formed at and be contained in the impeller the inside on the running shaft inserts and is arranged at depressed part on the casing, that have the cylindrical shape inner peripheral surface, the fixed orifice that forms by the gap between the cylindrical shape inner peripheral surface of the outer circumferential face of aforementioned cylindrical body and aforementioned depressed part
Bottom surface by aforementioned cylindrical body, the inner peripheral surface of this cylindrical body, the inner space of contiguous aforementioned cylindrical body, on casing outstanding the 1st protuberance that forms towards aforementioned bottom surface and the face of certain intervals arranged with it, and thrust-balancing chamber more outstanding more than aforementioned protuberance, that constitute around the outer circumferential face of ring-type the 2nd protuberance of running shaft
Aforementioned the 2nd protuberance is towards the front-end face of impeller the inside and the variable orifice of impeller the inside formation,
On aforementioned the 1st protuberance, form, around the annular groove of aforementioned running shaft, and
The equal splenium that is communicated with aforementioned annular groove and aforementioned depressed part.
2. thrust balancing device according to claim 1, it is characterized in that the summation of sectional area of described equal splenium of aforementioned claim 1 and axis normal direction and any one in the opening area of the described annular groove of aforementioned claim 1 on aforementioned the 1st protuberance, all the summation of the equalizing orifice opening area that is had greater than the described impeller of aforementioned claim 1.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP109720/1998 | 1998-04-20 | ||
| JP10972098 | 1998-04-20 | ||
| JP109720/98 | 1998-04-20 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1232928A true CN1232928A (en) | 1999-10-27 |
| CN1120937C CN1120937C (en) | 2003-09-10 |
Family
ID=14517524
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN99105578A Expired - Lifetime CN1120937C (en) | 1998-04-20 | 1999-04-14 | Thrust balance device |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP0952352B1 (en) |
| KR (1) | KR100295011B1 (en) |
| CN (1) | CN1120937C (en) |
| DE (1) | DE69922729T2 (en) |
| TW (1) | TW406166B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101113741B (en) * | 2006-07-26 | 2011-03-16 | 上海新沪电机厂有限公司 | Automatic balance device for shielding force at direction of pump spindle |
| CN109154300A (en) * | 2016-05-10 | 2019-01-04 | 萨乐锐伊塔洛工业有限公司 | Including support impeller and with the pump group of motor driver and thermo-mechanical drive |
| CN109281861A (en) * | 2018-11-28 | 2019-01-29 | 珠海格力电器股份有限公司 | A kind of axial force automatic balancing device, water pump and air conditioner |
| CN114483640A (en) * | 2022-01-25 | 2022-05-13 | 威乐(中国)水泵系统有限公司 | Impeller for centrifugal pump and compact industrial refrigeration pump |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4281614B2 (en) * | 2004-05-10 | 2009-06-17 | 株式会社日立プラントテクノロジー | Pump device |
| CN100368689C (en) * | 2004-09-16 | 2008-02-13 | 北京化工大学 | Differential thrust balance device for rotary fluid machinery |
| US8529191B2 (en) * | 2009-02-06 | 2013-09-10 | Fluid Equipment Development Company, Llc | Method and apparatus for lubricating a thrust bearing for a rotating machine using pumpage |
| KR101509814B1 (en) * | 2009-12-02 | 2015-04-06 | 현대자동차주식회사 | Cooling water pump having improved impeller struture |
| DE102009060549A1 (en) * | 2009-12-23 | 2011-06-30 | Wilo Se, 44263 | EC motor centrifugal pump |
| KR101700332B1 (en) | 2015-07-29 | 2017-02-14 | 한국해양대학교 산학협력단 | Apparatus for Decreasing Thrust of Radial Inflow Turbine |
| US11085457B2 (en) | 2017-05-23 | 2021-08-10 | Fluid Equipment Development Company, Llc | Thrust bearing system and method for operating the same |
| US10801512B2 (en) | 2017-05-23 | 2020-10-13 | Vector Technologies Llc | Thrust bearing system and method for operating the same |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4938641B1 (en) * | 1970-08-06 | 1974-10-19 | ||
| US5320482A (en) * | 1992-09-21 | 1994-06-14 | The United States Of America As Represented By The Secretary Of The Navy | Method and apparatus for reducing axial thrust in centrifugal pumps |
| DE4421888A1 (en) * | 1994-06-23 | 1996-01-04 | Klein Schanzlin & Becker Ag | Device for axial thrust compensation in centrifugal pumps |
-
1999
- 1999-04-14 CN CN99105578A patent/CN1120937C/en not_active Expired - Lifetime
- 1999-04-14 TW TW088105939A patent/TW406166B/en not_active IP Right Cessation
- 1999-04-16 KR KR1019990013435A patent/KR100295011B1/en not_active IP Right Cessation
- 1999-04-19 DE DE69922729T patent/DE69922729T2/en not_active Expired - Lifetime
- 1999-04-19 EP EP99107770A patent/EP0952352B1/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101113741B (en) * | 2006-07-26 | 2011-03-16 | 上海新沪电机厂有限公司 | Automatic balance device for shielding force at direction of pump spindle |
| CN109154300A (en) * | 2016-05-10 | 2019-01-04 | 萨乐锐伊塔洛工业有限公司 | Including support impeller and with the pump group of motor driver and thermo-mechanical drive |
| CN109281861A (en) * | 2018-11-28 | 2019-01-29 | 珠海格力电器股份有限公司 | A kind of axial force automatic balancing device, water pump and air conditioner |
| CN114483640A (en) * | 2022-01-25 | 2022-05-13 | 威乐(中国)水泵系统有限公司 | Impeller for centrifugal pump and compact industrial refrigeration pump |
Also Published As
| Publication number | Publication date |
|---|---|
| EP0952352B1 (en) | 2004-12-22 |
| DE69922729D1 (en) | 2005-01-27 |
| TW406166B (en) | 2000-09-21 |
| EP0952352A2 (en) | 1999-10-27 |
| KR19990083231A (en) | 1999-11-25 |
| CN1120937C (en) | 2003-09-10 |
| KR100295011B1 (en) | 2001-07-12 |
| EP0952352A3 (en) | 2001-05-30 |
| DE69922729T2 (en) | 2005-12-01 |
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