CN203248387U - Hot water circulating pump axial force automatic dynamic balance structure - Google Patents
Hot water circulating pump axial force automatic dynamic balance structure Download PDFInfo
- Publication number
- CN203248387U CN203248387U CN 201320243971 CN201320243971U CN203248387U CN 203248387 U CN203248387 U CN 203248387U CN 201320243971 CN201320243971 CN 201320243971 CN 201320243971 U CN201320243971 U CN 201320243971U CN 203248387 U CN203248387 U CN 203248387U
- Authority
- CN
- China
- Prior art keywords
- impeller
- balance disc
- axial force
- hot water
- circulating pump
- 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.)
- Expired - Fee Related
Links
Images
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The utility model discloses a hot water circulating pump axial force automatic dynamic balance structure. The clearance between a right-angle balance disk and a balance disk sleeve is increased or reduced through the movement of an impeller on a main shaft, so that mean pressure in the cavity of an impeller rear cover plate and mean pressure in a balance disk leakage path are adjusted, and therefore acting force acting on the impeller rear cover plate is changed, acting force on the front cover plate and the rear cover plate of the impeller is made to be identical, and therefore generated axial force can be balanced no matter how the acting force on the front cover plate and the rear cover plate of the impeller is changed, and the aim of impeller axial force automatic dynamic balance is achieved. Through the technical scheme, the axial force generated by the impeller can be completely balanced, the hot water circulating pump axial force automatic dynamic balance structure is simple and reliable in structure, the service life of a bearing is greatly prolonged, and the hot water circulating pump axial force automatic dynamic balance structure is of great significance in the study of a safe and reliable hot water circulating pump with long service life.
Description
Technical field
The utility model relates to the technical field of pump, refers in particular to a kind of hot water circulating pump axial force homeostasis structure.
Background technique
In the industries such as metallurgy, electric power, light textile, oil, chemical industry, chemical fertilizer, pharmacy, papermaking, environmental protection, rubber, heating, UTILIZATION OF VESIDUAL HEAT IN and nuclear energy, all can use the hot water circulating pump of carrying thermal medium.Because what hot water circulating pump was carried is high temperature media, medium temperature generally is higher than 220 ℃, and high temperature media will the heat transferred pump, cause that the bulk temperature of pump is increased to more than 220 ℃, so also just affected each component working environment of pump, the safe operation of pump has been affected.Especially affect larger on the shaft seal of pump and the reliable operation of bearing.
The main shaft supporting mode of hot water circulating pump is that an end adopts 1 group of metal roller bearing, and the other end adopts guide bearing, and the operating temperature of common metal roller bearing is the highest can not to be higher than 75 ℃, and too high operating temperature can shorten the mission of bearing, even can damage bearing.The main cause that bearing temperature rise produces is the heat that ambient temperature and bearing operation produce, the heat that bearing operation produces is directly proportional with the power on being added in bearing, therefore, alleviate the power that acts on the bearing and just can alleviate the bearing heating amount, reduce the temperature that bearing working produces.
The larger axis that ordinary hot water-circulating pump impeller produces in rotary course is born by bearing to power, can cause the bearing heating amount to strengthen, the temperature of rising bearing, add the medium temperature height that hot water circulating pump is carried, cause again the ambient temperature of bearing higher, like this, make easily the operating temperature of bearing surpass allowable value, affect the working life of bearing, thereby affect the reliability of hot water circulating pump, in order to improve the reliability of hot water circulating pump, the temperature that reduces bearing is necessary, and present hot water circulating pump axial force balancing method is improved, make it not act on the bearing fully, greatly alleviate the active force on the bearing, thereby reduce the temperature of bearing, the working life of improving bearing.
The model utility content
The technical solution of the utility model is a kind of hot water circulating pump axial force homeostasis structure, its purpose is intended to overcome the deficiency of present hot water circulating pump axial force balance, propose axial force and reach the method for homeostasis by impeller from main shaft, moving about, solve larger axis and be added in the technical problem that causes on the bearing that bearing temperature raises, the working life that can improve the hot water circuit pump bearing to power.
Know-why of the present utility model: by impeller moving about on main shaft, increase or reduce the gap between right angle Balance disc and the Balance disc cover, to adjust middle pressure in the back shroud of impeller cavity
P 2 With middle pressure in the Balance disc leakage way
P 3 Size, thereby change the active force act on back shroud of impeller, make that active force equates on the front and rear cover plate of impeller, thus no matter on the impeller front and rear cover plate active force how to change, the axial force that produces can be carried out balance, reaches the purpose of axial force of impeller homeostasis.
The technological scheme that the utility model is concrete: during work, main shaft is by the rotation of key impeller, the impeller of rotation passes to energy in the medium of conveying, medium just has higher pressure to impeller outlet, because impeller outlet is communicated with impeller front and rear cover plate cavity, this pressure will act on the impeller front and rear cover plate and produce active force, and also unequal because of the active force that produces, the difference between them is exactly the axial force that impeller produces.
The technical solution of the utility model is that choma is provided with the right angle Balance disc behind the impeller of described pump impeller; Connecting base is provided with the Balance disc cover.Form between choma and the increasing back sealing ring behind seal ring leakage, the impeller before forming between impeller preoral loop and the front seal ring and be provided with Balance disc leakage, right angle Balance disc and the Balance disc gap between overlapping between increasing back sealing ring leakage, right angle Balance disc and the Balance disc cover; The front shroud of impeller cavity is communicated with impeller inlet by front seal ring leakage, impeller inlet is communicated with refluxing chamber by return port, refluxing chamber is connected with the increasing back sealing ring leakage by the gap between right angle Balance disc and the Balance disc cover, and the increasing back sealing ring leakage is connected with impeller outlet.
Refluxing chamber is realized the front shroud cavity of impeller and being communicated with of back shroud of impeller cavity by return port, leakage, gap etc.
Axial force balancing method is: the first situation, active force on the front shroud of impeller is greater than the active force on the back shroud, because impeller set is on main shaft, axially unfixing, be in quick condition, will promote like this impeller to the right direction move, gap between right angle Balance disc and the Balance disc cover is reduced, cause the leakage rate in gap also to reduce, leakage rate reduces middle pressure and the interior middle pressure of Balance disc leakage way that has improved in the back shroud of impeller cavity, can improve so again the active force on the back shroud, impeller continues to the right that direction moves, and the middle pressure in the back shroud of impeller cavity and the middle pressure in the Balance disc leakage way further improve, cause active force increase on the back shroud of impeller, until active force equates on the impeller front and rear cover plate, at this moment, impeller reaches again new balance.
The second situation, active force on the front shroud of impeller is less than the active force on the back shroud, promotion impeller to the left direction moves, gap between right angle Balance disc and the Balance disc cover is increased, the gap increase causes leakage rate also to strengthen, and the leakage rate increase reduces middle pressure and the middle pressure in the Balance disc leakage way in the back shroud of impeller cavity, has reduced like this active force on the back shroud, impeller continues to the left that direction moves, the mean pressure in the back shroud of impeller cavity
P 2 With the mean pressure in the Balance disc leakage way
P 3 Further reduce, cause that active force reduces on the back shroud of impeller, until active force equates on the front and rear cover plate of impeller, at this moment, impeller reaches again new balance, no matter how active force changes on the impeller front and rear cover plate, and the axial force of generation can be carried out balance by impeller moving about on main shaft, reaches the purpose of axial force homeostasis.
The utility model has the advantages that: the axial force that can the complete equilibrium impeller produces, and simple in structure, reliable, the working life of greatly improving bearing, to research safety, reliable, the long lifetime hot water circulating pump is significant.
Description of drawings
Accompanying drawing 1 is the longitudinal section tectonic maps of the guide bearing structure of hot water circulating pump.
1 is screw among the figure, the 2nd, impeller nut, the 3rd, the shaft extension screw thread, the 4th, impeller inlet, the 5th, return port, the 6th, the impeller preoral loop, the 7th, front seal ring leakage way, the 8th, front seal ring, the 9th, refluxing chamber, the 10th, the front shroud of impeller cavity, the 11st, choma behind the impeller, the 12nd, front shroud of impeller, the 13rd, impeller, the 14th, impeller outlet, the 15th, the pump housing, the 16th, back shroud of impeller, the 17th, the back shroud of impeller cavity, the 18th, rear pump cover, the 19th, increasing back sealing ring, the 20th, the increasing back sealing ring leakage way, the 21st, the right angle Balance disc, the 22nd, A screw, the 23rd, rear closed chamber, the 24th, the Balance disc cover, the 25th, the Balance disc leakage way, the 26th, B screw, the 27th, labyrinth channel, the 28th, the annulus area, the 29th, the gap between right angle Balance disc and the Balance disc cover, the 30th, connecting base, the 31st, key, the 32nd, main shaft, the 33rd, bearing support, the 34th, bearing, the 35th, short sleeve, the 36th, stripped nut.
Embodiment
Below in conjunction with Fig. 1 embodiment of the present utility model is described further.
As shown in Figure 1, connecting base 30 connects with bearing support 33, bearing 34 is installed in the bearing support 33, rear pump cover 18 connects with connecting base 30, main shaft 32 passes connecting base 30 and is set in the bearing 34, short sleeve 35 is enclosed within on the main shaft 32, stripped nut 36 is spun on the main shaft 32 and withstands bearing 34 by short sleeve 35, main shaft 32 is axially fixed on the bearing 34, Balance disc cover 24 is fixed on the connecting base 30 by B screw 26, and increasing back sealing ring 19 is installed in the rear pump cover 18, and key 31 is installed on the main shaft 32, impeller 13 is enclosed within on the main shaft 32, between impeller 13 and the main shaft 32 key 31 is housed and circumferentially fixes.Right angle Balance disc 21 is fixed on behind the impeller on the impeller 13 on the choma 11 by A screw 22, impeller 13 is axially unfixing, choma 11 forms increasing back sealing ring leakage way 20 with increasing back sealing ring 19 behind the impeller, form Balance disc leakage way 25 between right angle Balance disc 21 and the Balance disc cover 24, be provided with labyrinth channel 27 between the right angle side of right angle Balance disc 21 and Balance disc cover 24, impeller nut 2 is spun on the shaft extension screw thread 3 of main shaft 32, screwing screw 1 is fixed on impeller nut 2 on the shaft extension screw thread 3, front seal ring 8 is installed on the pump housing 15, the pump housing 15 and rear pump cover 18 are connected and fixed seal ring leakage way 7 before forming between the impeller preoral loop 6 on the impeller 13 and the front seal ring 8.
During work, main shaft 32 is by 13 rotations of key 31 impeller, impeller 13 rotations pass to energy in the medium of conveying, medium just has higher pressure at impeller outlet 14, and impeller inlet 4 places are low pressure area, between impeller outlet 14 and impeller inlet 4, form pressure reduction, under the effect of pressure reduction, will produce in front shroud of impeller 12 positions from impeller outlet 14 by the leakage to impeller inlet 4 of front shroud of impeller cavity 10, front seal ring leakage way 7, the gap of front seal ring leakage way 7 is very little, plays the effect of throttling anti-leak; Refluxing chamber 9 is by return port 5 and impeller inlet 4 UNICOMs, pressure in the refluxing chamber 9 and impeller inlet 4 interior pressure equate, same under the effect of pressure reduction, will produce in back shroud of impeller 16 positions from impeller outlet 14 by the leakage to refluxing chamber 9 of back shroud of impeller cavity 17, increasing back sealing ring leakage way 20, Balance disc leakage way 25, labyrinth channel 27, increasing back sealing ring leakage way 20, Balance disc leakage way 25 and labyrinth channel 27 the gap very little, play the effect of throttling anti-leak.
Axial force balancing method is: the area of note front shroud of impeller 12 is
A 1 , the middle pressure in the front shroud of impeller cavity 10 is
P 1 , the area of back shroud of impeller 16 is
A 2 , the middle pressure in the back shroud of impeller cavity 17 is
P 2 , the annulus area 28 in the Balance disc leakage way 25 is
A 3 , the middle pressure in the Balance disc leakage way 25 is
P 3 , pressure-acting at the active force that front shroud of impeller 12 produces is
A 1 *
P 1 , pressure-acting at the active force that back shroud of impeller 16 produces is
A 2 *
P 2 +
A 3 *
P 3 , in design conditions, active force equates on the front and rear cover plate of impeller 13, has
A 1 *
P 1 =
A 2 *
P 2 +
A 3 *
P 3 , at this moment, impeller 13 is static not mobile, and this situation is difficult to keep, and the most cases pump is under the off-design behaviour and moves, and like this, active force is with regard to unequal generation axial force on the front and rear cover plate of impeller 13.Be divided into two kinds of situations: the first situation, on the front shroud 12 of impeller 13 there be greater than active force on the back shroud 16 active force:
A 1 *
P 1 ＞
A 2 *
P 2 +
A 3 *
P 3 Because impeller 13 is enclosed within on the main shaft 32, axially unfixing, be in quick condition, will promote like this impeller 13 moves to the right direction among Fig. 1, gap 29 between right angle Balance disc and the Balance disc cover is reduced, and the gap reduces to cause leakage rate also to reduce, and leakage rate reduces the middle pressure that has improved in the back shroud of impeller cavity 17
P 2 With the middle pressure in the Balance disc leakage way 25
P 3 , can improve active force on the back shroud so again
A 2 *
P 2 +
A 3 *
P 3 , impeller 13 continues to the right that direction moves, the middle pressure in the back shroud of impeller cavity 17
P 2 With the middle pressure in the Balance disc leakage way 25
P 3 Further improve, cause also further increase of active force on the back shroud of impeller 16, until active force equates on the front and rear cover plate of impeller 13, that is:
A 1 *
P 1 =
A 2 *
P 2 +
A 3 *
P 3 , at this moment, impeller 13 reaches again new balance.
The second situation, on the front shroud 12 of impeller 13 there be less than active force on the back shroud 16 active force:
A 1 *
P 1 ＜
A 2 *
P 2 +
A 3 *
P 3 , promote impeller 13 and move to the left direction among Fig. 1, the gap 29 between right angle Balance disc and the Balance disc cover is increased, the gap increase causes leakage rate also to strengthen, and the leakage rate increase makes the middle pressure in the back shroud of impeller cavity 17
P 2 With the middle pressure in the Balance disc leakage way 25
P 3 Reduce, reduced like this active force on the back shroud
A 2 *
P 2 +
A 3 *
P 3 , impeller 13 continues to the left that direction moves, the middle pressure in the back shroud of impeller cavity 17
P 2 With the middle pressure in the Balance disc leakage way 25
P 3 Further reduce, cause also further minimizing of active force on the back shroud of impeller 16, until active force equates on the front and rear cover plate of impeller 13, that is:
A 1 *
P 1 =
A 2 *
P 2 +
A 3 *
P 3 , at this moment, impeller 13 reaches again new balance.Analyze thus and know, no matter how active force changes on the front and rear cover plate of impeller 13, and the axial force of generation can be carried out balance by impeller 13 moving about on main shaft 32, thereby reaches the purpose of hot water circulating pump axial force homeostasis.
Claims (5)
1. hot water circulating pump axial force homeostasis structure, described pump is provided with right angle Balance disc (21), Balance disc cover (24), it is characterized in that, form between choma (11) and the increasing back sealing ring (19) behind seal ring leakage (7), the impeller before forming between impeller preoral loop (6) and the front seal ring (8) and be provided with Balance disc leakage (25), right angle Balance disc and the Balance disc gap (29) between overlapping between increasing back sealing ring leakage (20), right angle Balance disc (21) and the Balance disc cover (24); Front shroud of impeller cavity (10) is communicated with impeller inlet (4) by front seal ring leakage (7), impeller inlet (4) is communicated with refluxing chamber (9) by return port (5), refluxing chamber (9) is connected with increasing back sealing ring leakage (20) by the gap (29) between right angle Balance disc and the Balance disc cover, and increasing back sealing ring leakage (20) is connected with impeller outlet (14).
2. hot water circulating pump axial force homeostasis structure according to claim 1 is characterized in that, right angle Balance disc (21) is fixed on behind the impeller on the impeller (13) on the choma (11) by A screw (22).
3. hot water circulating pump axial force homeostasis structure according to claim 1 is characterized in that Balance disc cover (24) is fixed on the connecting base (30) by B screw (26).
4. hot water circulating pump axial force homeostasis structure according to claim 1 is characterized in that, is provided with labyrinth channel (27) between the right angle side of right angle Balance disc (21) and Balance disc cover (24).
5. hot water circulating pump axial force homeostasis structure according to claim 1, it is characterized in that: impeller (13) is set on the main shaft (32), circumferentially fixes by key (31) between impeller (13) and the main shaft (32).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320243971 CN203248387U (en) | 2013-05-08 | 2013-05-08 | Hot water circulating pump axial force automatic dynamic balance structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320243971 CN203248387U (en) | 2013-05-08 | 2013-05-08 | Hot water circulating pump axial force automatic dynamic balance structure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203248387U true CN203248387U (en) | 2013-10-23 |
Family
ID=49374829
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320243971 Expired - Fee Related CN203248387U (en) | 2013-05-08 | 2013-05-08 | Hot water circulating pump axial force automatic dynamic balance structure |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203248387U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103291645A (en) * | 2013-05-08 | 2013-09-11 | 江苏大学 | Automatic dynamic axial force balancing structure of hot water circulating pump |
-
2013
- 2013-05-08 CN CN 201320243971 patent/CN203248387U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103291645A (en) * | 2013-05-08 | 2013-09-11 | 江苏大学 | Automatic dynamic axial force balancing structure of hot water circulating pump |
| CN103291645B (en) * | 2013-05-08 | 2016-01-20 | 江苏大学 | A kind of hot water circulating pump axial force homeostasis structure |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103573713A (en) | High-temperature self-cooling hot water circulating pump | |
| CN203146430U (en) | High-temperature self-cooling hot water circulation pump | |
| CN103291645A (en) | Automatic dynamic axial force balancing structure of hot water circulating pump | |
| CN202612183U (en) | Bearing body part used for high-temperature and high-voltage hot water circulation pump | |
| CN203248387U (en) | Hot water circulating pump axial force automatic dynamic balance structure | |
| CN103644145B (en) | A kind of hot water circulating pump suspension body of coil pipe cooling structure | |
| CN104197025B (en) | A kind of combination seal water-cooling bearing block of large fan | |
| CN203023134U (en) | Multistage drainage pump | |
| CN201972955U (en) | Dynamic and static clearance wedge groove arc sealing structure for nuclear main pump | |
| CN107725113B (en) | Two-stage cantilever type axial flow expander | |
| CN204083254U (en) | A kind of combination seal water-cooling bearing block of large fan | |
| CN103277146A (en) | Symmetrical lateral tooth steam sealing structure | |
| CN103758581B (en) | High speed turbine gland seal system for power circulation of organic working medium | |
| CN105257344B (en) | A kind of encapsulating method of steam turbine single current high pressure cylinder front steam seal | |
| CN202483895U (en) | Multiple-group magnetic drive pump | |
| CN203847394U (en) | Self-balancing multistage centrifugal pump with balanced cooling structure | |
| CN205190245U (en) | Resistant dry grinding magnetic drive pump | |
| CN204663957U (en) | High Temperature High Pressure forces hot water circuit mechanical sealing device used for pump | |
| CN204164020U (en) | The axial force balance mechanism of boiler feed pump in a kind of waste incineration and generating electricity system | |
| CN204186654U (en) | A kind of novel centrifugal double shrouded wheel axial force balance structure | |
| CN103075204B (en) | Back steam seal device of steam turbine | |
| CN202628534U (en) | Small-flow double-cylinder horizontal multiple-stage centrifugal pump | |
| CN203796332U (en) | High-speed turbine shaft gland system for power cycling of organic working media | |
| CN203892229U (en) | Bearing structure for low-pressure forced lubrication of high-speed oil conveying pipeline pump | |
| CN201225314Y (en) | High temperature resistant and ultra-high pressure kinetic pressure balance non-leakage pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20131023 Termination date: 20140508 |