CN107448412A - Impeller - Google Patents
Impeller Download PDFInfo
- Publication number
- CN107448412A CN107448412A CN201710399186.6A CN201710399186A CN107448412A CN 107448412 A CN107448412 A CN 107448412A CN 201710399186 A CN201710399186 A CN 201710399186A CN 107448412 A CN107448412 A CN 107448412A
- Authority
- CN
- China
- Prior art keywords
- blade
- impeller
- exterior region
- radius
- suction
- 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.)
- Pending
Links
Classifications
-
- 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
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention provides a kind of energy loss for flowing through the fluid of stream between blade and reduced and the impeller with the high efficiency of pump.The impeller is centrifugal pump possessed impeller, and on the thickness of blade, the thickness of the exterior region of blade is more than 2.8 times of the thickness of hinder marginal part.
Description
Technical field
The present invention relates to a kind of centrifugal pump or diagonal pumps possessed impeller.
Background technology
Centrifugal pump and diagonal pumps rotate impeller by driving machine, and kinetic energy is supplied to the fluid of suction, should by pump case
Kinetic energy is converted to pressure energy and discharge.For example, patent document 1 discloses the angle of a kind of inlet angle to blade and blade
The impeller (impeller) studied.
Prior art literature
Patent document
Patent document 1：Japanese Unexamined Patent Application Publication 2014-511973 publications
Invent problem to be solved
Such centrifugal pump and diagonal pumps are with the rotating speed high speed for making impeller, the energy loss increase of impeller, the efficiency of pump
Significantly reduce.
The content of the invention
The present invention is to propose in view of the above circumstances, and its object is to provide a kind of fluid for flowing through stream between blade
Energy loss reduce, have the high efficiency of pump impeller.
Means for solving the problems
In order to reach above-mentioned purpose, impeller of the invention is characterised by, the impeller is centrifugal pump or diagonal pumps
Possessed impeller, on the thickness of blade, the thickness of the exterior region of the blade is the thickness of the hinder marginal part of the blade
More than 2.8 times.
It is the 2.8 of the thickness of hinder marginal part in the thickness of the exterior region of blade it was found from the result of the wholwe-hearted research of inventor
When more than times, the energy loss for flowing through the fluid of stream between blade is reduced, and the efficiency of pump improves.
In addition, in the present invention, it is preferred that the distance along the pressure face with the blade and with the blade
When the exterior region is set to 0 and the hinder marginal part is set into 1 by the equidistant imagining center line of suction surface, by the impeller
Axis of rotation as center angle of spread ratio be 0 at least 0.1 in the range of, the constant thickness of the blade, particularly preferably
, in the distance along the pressure face with the blade and the equidistant imagining center line with the suction surface of the blade
When the exterior region being set into 0 and the hinder marginal part being set into 1, in the angle of spread ratio using the axis of rotation of the impeller as center
In the range of 0 to 0.2, the constant thickness of the blade.
Also, in the present invention, it is preferred that the distance along the pressure face with the blade and with the blade
When the exterior region is set to 0 and the hinder marginal part is set into 1 by the equidistant imagining center line of suction surface, by the impeller
Axis of rotation as center angle of spread ratio be 0.3 to 0.7 in the range of, the thickness of the blade is lateral from the exterior region
The hinder marginal part side consistently reduces.In addition, in the present invention, it is preferred that along the pressure face with the blade away from
The exterior region is set to 0 from the equidistant imagining center line with the suction surface with the blade and sets the hinder marginal part
For 1 when, using the axis of rotation of the impeller as center angle of spread ratio be 0.15 to 0.3 in the range of, the thickness of the blade
Degree has flex point.Moreover, in the present invention, it is preferred that the thickness of the exterior region is the diameter of the suction inlet of the impeller
0.1~0.3 times.
In the present invention, it is preferred that the impeller also has wheel hub and shield, it is described in the exterior region of the blade
The radius of the hub side of blade is 0.30~0.55 times of the radius of the shroud.
According to above-mentioned structure, in the exterior region of blade, make the hub side of blade compared to blade shroud relatively
Positioned at radially inner side, so that in the hub side of the blade as the radial position close to axis of rotation, impeller can will be flowed into
Fluid guide earlier to being surrounded by blade, wheel hub and shield and stream between the blade that forms, therefore, and as from rotation
The fluid for flowing into impeller is guided the situation to stream between blade to compare by the shroud of the blade of the remote radial position in axle center, energy
It is enough the reduction of axle power is improved the efficiency of pump with same traffic, total head, and the effect for suppressing vibration can be improved.Because in leaf
The fluid that the exterior region of piece flows into impeller swimmingly guided to stream between blade thus the fluid for being connected on shield stream
It is difficult to produce disorder in dynamic, because friction loss is reduced can aid in the reduction of axle power.
In the present invention, it is preferred that the impeller also has wheel hub, in the exterior region of the blade, the blade
The radius of the hub side is 0.30~0.55 times of the radius for sucking sleeve side, and the suction sleeve is set to across the blade
It is and relative with the wheel hub.
According to above-mentioned structure, in the exterior region of blade, make hub side being configured to across leaf compared to blade of blade
Piece and the suction sleeve side relative with wheel hub is located opposite from radially inner side, so as to as close to axis of rotation radial position
Blade hub side, the fluid for flowing into impeller can be guided earlier to by blade, wheel hub and suction sleeve surround and
Stream between the blade of composition, therefore, with that will be flowed into the suction sleeve side of the blade as the radial position remote from axis of rotation
Fluid to impeller guides the situation to stream between blade to compare, and reduce with same traffic, total head axle power makes pump
Efficiency improves, and can improve the effect for suppressing vibration.Because there is gap in unshrouded impeller, institute between blade and suction sleeve
To produce leakage from the gap.When the leakage increases, friction loss increases, and causes axle power to rise.But as described above, structure
The fluid for flowing into impeller is guided to stream between blade earlier as in the hub side of blade, so as to suck the work(of sleeve side
Relatively reduce, therefore the disorderly reduction in the flowing of fluid, leakage are reduced.Because leakage is reduced, so as to identical complete
Lift, axle power convey more flows, therefore can improve the efficiency of pump.
In the present invention, it is preferred that in the exterior region, the hub side of the blade and the shroud or
The radius of the pars intermedia of the suction sleeve side is the 0.50~0.65 of the radius of the shroud or the suction sleeve side
Times.
It is 0.30~0.55 times of the radius of shroud or suction sleeve side in the radius of the exterior region hub side of blade
When, it is shroud or suction sleeve side in the radius for the pars intermedia that exterior region hub side and shroud either suck sleeve side
0.50~0.65 times of radius, on such blade, at least from the lateral shroud of wheel hub or suck sleeve side in exterior region
The bending of blade be set as convex form in negative pressure surface side, be set as concave shape in pressure surface side.That is, it is able to ensure that leaf in pressure surface side
Stream is wide between piece.
In the present invention, it is preferred that in the exterior region, the radius of the blade is from the lateral shield of the wheel hub
Side or the suction sleeve side little by little increase.
Blade at least exterior region by from the bending of the blade of the lateral shroud of wheel hub or suction sleeve side in suction surface
Side is set as smooth convex form, so as to suppress to make the movement disorder for the fluid for being sucked into impeller while fluid is guided
To stream between blade.
In the present invention, it is preferred that in the exterior region, the shroud of the blade or the suction sleeve
The radius of side is equal with the radius of the suction inlet of the impeller.
The shroud or suction sleeve side for making the exterior region of suction inlet and blade approach, so as to be inhaled from suction inlet
Guide to stream between blade the smooth fluid entered.If in addition, the shroud of exterior region or the radius leaf of suction sleeve side
0.9~1.2 times or so of scope of the radius of the suction inlet of wheel, the then radius for being considered as both are equal.
In the present invention, it is preferred that in the exterior region, the shroud of the blade or the suction sleeve
Side is located in front of direction of rotation relative to the hub side.
Between the blade of turbine pump possessed impeller as centrifugal pump and diagonal pumps in stream, approximately along stream
On the basis of the main flow of flowing, the stripping of the two-dimensional current due to the barometric gradient between blade in stream etc., vortex and flowing is produced
From etc., this turns into one of the reason for efficiency reduces.Blade is configured in exterior region shroud or suction sleeve side relative to wheel
Hub side is located in front of direction of rotation, so as to reduce the generation for turning into phenomenon the reason for reducing efficiency, therefore can improve
Efficiency.
In the present invention, it is preferred that in the hinder marginal part of the blade, the shroud of the blade or the suction
Enter sleeve side relative to the hub side to be located in front of direction of rotation.
In the hinder marginal part of blade, it is located at same position in a rotational direction in hub side and shroud or suction sleeve side
When, sleeve from the lateral shroud of wheel hub or is sucked by hinder marginal part of the fluid force caused by impeller in blade in the tongue of pump case
Side disposably acts on, therefore produces flexure in blade, by the disorder of the balance of direction of rotation caused by the flexure of blade, so that
Uneven radial load acts on bearing, turn into shorten bearing life-span the reason for.
Blade is configured to be located at direction of rotation relative to hub side in the hinder marginal part shroud of blade or suction sleeve side
Front, so as to the tongue of pump case by fluid force caused by impeller blade hinder marginal part from the lateral shroud of wheel hub or suction
Enter sleeve side to act on successively, therefore flow out while smooth fluid can be made, therefore the generation of problem as described above can be suppressed.
In the present invention, it is preferred that possesses leaf described in two panels in the relative position of the axis of rotation across the impeller
Piece.
When the piece number of blade is more, the efficiency of pump improves, and still, because stream narrows between blade, foreign matter easily blocks.
On the other hand, when blade is a piece of, it can be ensured that stream is wide between blade, but is produced in the balance around axis of rotation uneven
Weighing apparatus, pulsation is produced in discharge due to this, the efficiency of pump reduces.The piece number of blade is set as two panels, so as between blade stream with
Blade is a piece of situation compared to narrowing, but fully ensure on one side foreign matter by property while making the balance around axis of rotation
Do not produce it is unbalanced, therefore the efficiency of pump improve.
In the present invention, it is preferred that foreign matter by footpath in more than 76mm.
When centrifugal pump and diagonal pumps to be used in the conveying of sewage dirt, the problem of being frequently accompanied by the occlusion of foreign matter.
For fluid of the bull ladle containing foreign matter, the foreign matter from the point of view of the requirement of slave unit side desirably more than 76mm (about 3 inches) passes through footpath.
Therefore, the foreign matter of impeller is set as more than 76mm by footpath, so as to make between blade stream clip the possibility drop of foreign matter
It is low.
In addition, foreign matter is can be by the maximum gauge of the foreign matter of stream between blade by footpath.Foreign matter percent of pass is from tool
What the discharge diameter and foreign matter of the pump of standby impeller were derived by footpath.
Brief description of the drawings
Fig. 1 is the explanation figure of the impeller of first embodiment.
Fig. 2 is the major part top view of impeller.
Fig. 3 is the explanation figure of the thickness of blade.
Fig. 4 is the explanation figure of the shape of blade.
Fig. 5 is the comparison figure of the efficiency of pump.
Fig. 6 is the explanation figure of the shape of blade.
Fig. 7 is the comparison figure of the efficiency of pump.
Fig. 8 is the explanation figure of the impeller of second embodiment.
Symbol description
1：Centrifugal pump
10：Impeller
11：Blade
13：Wheel hub
15：Shield
19：Suction inlet
20：Exterior region
21：Hinder marginal part
30：Impeller
31：Blade
33：Wheel hub
35：Suck sleeve
39：Suction inlet
40：Exterior region
C：Axis of rotation
r：Radius
ri：Radius
rm：Radius
ro：Radius
rs：Radius
Embodiment
While one side illustrates to the embodiment of the impeller of the present invention referring to the drawings.
In addition, in the following description, the impeller using the present invention be centrifugal pump possessed centrifugal impeller situation as
Example and illustrate.
Fig. 1 represents the pump case 2 of impeller 10 and covering impeller 10 that centrifugal pump 1 possesses.Impeller 10 is installed on electricity (not shown)
The output shaft of motivation and around axis of rotation C rotate.
Pump case 2, which internally contains, to be connected and fixed on the motor field frame of the motor in the state of impeller 10 and (does not scheme
Show) end.In pump case 2, being provided with the axis of rotation C of the output shaft of the motor flows into fluid from outside
Inflow entrance 3, impeller 10 radial outside be provided with by the fluid of suction to outside discharge flow export 4.
In the present embodiment, impeller 10 is the so-called double shrouded wheel for having blade 11, wheel hub 13 and shield 15.
Wheel hub 13 possesses the central fitting portion 16 for the output shaft of the motor to be embedded in the wheel hub 13,
Wheel hub surface 17 from fitting portion 16 to the remote position of radial outside to radial outside from being somewhat bent to form.Wheel hub surface 17 is formed
For the part of radially inner side is located at the side of suction inlet 19 of impeller 10 along axis of rotation C, outer with being radially oriented from radially inner side
Side is along suction inlets 19 of the axis of rotation C away from impeller 10.
Shield 15 be formed as with the same diameter of wheel hub 13, possess suction inlet 19 in the center of shield 15, shield face 18 is from suction
Entrance 19 is bent to form to radial outside.Shield face 18 is formed as, the side of suction inlet 19 with along axis of rotation C away from wheel hub 13
Mode extends, with outside is radially oriented from radially inner side, along axis of rotation C close to wheel hub 13.
In meridian plane, blade 11 from the side of wheel hub 13 as blade 11 and the intersection of wheel hub surface 17 to as blade 11 with
Width W between the side of shield 15 of the intersection in shield face 18, little by little narrows from radially inner side to radial outside.That is, from entrance
Width W0To exit width W1Little by little narrow.In addition, represent the side of wheel hub 13 of blade 11 and the pars intermedia of the side of shield 15 with Wm
Width.
In the present embodiment, between wheel hub surface 17 and shield face 18, arranged across position relative axis of rotation C
There is two panels blade 11.
In exterior region 20, the radius ri of the side of wheel hub 13 of blade 11 is about 0.45 times of the radius ro of the side of shield 15, wheel
The radius rm of the pars intermedia of the side of hub 13 and the side of shield 15 is about 0.58 times of the radius ro of the side of shield 15, the radius of the side of shield 15
Ro is equal with the radius rs of the suction inlet 19 of impeller 10.In exterior region 20, the radius r of blade 11 is from the lateral side of shield 15 of wheel hub 13
Little by little increase.In the present embodiment, the radius ro of the side of shield 15 of exterior region 20 is the radius rs of the suction inlet of impeller 10
Substantially 1.0 times.If in addition, the radius ro of the side of shield 15 of exterior region 20 the suction inlet of impeller 10 radius rs 0.9~
It is equal to be then considered as both in the range of 1.2 times.
In addition, in exterior region 20, the side of shield 15 of blade 11 is located in front of direction of rotation relative to the side of wheel hub 13, at least existed
Exterior region 20, blade 11 are set as smooth convex form, pressure face 11p sides in suction surface 11n sides from the lateral side of shield 15 of wheel hub 13
It is set as smooth concave shape.In addition, from output shaft side, the motor is to rotate forward clockwise.
In hinder marginal part 21, the side of shield 15 of blade 11 is located in front of direction of rotation relative to the side of wheel hub 13.
Pressure face 11p and suction surface 11n, the pressure face 11p and suction surface 11n by adjacent two panels blade 11 of impeller 10
Between wheel hub surface 17 and shield face 18 surround space be set as stream 22 between blade.
In the present embodiment, between the suction inlet 19 and blade of impeller 10 foreign matter of stream 22 by footpath in 76mm (about 3 English
It is very little) more than.The diameter for possessing the flow export 4 of the centrifugal pump 1 of impeller 10 is 150mm.Therefore, foreign matter percent of pass is set as about
50%.
In addition, foreign matter by footpath be can by the maximum gauge of the foreign matter of stream between blade 22, foreign matter percent of pass be from
Possess the diameter of the flow export 4 of the centrifugal pump 1 of impeller 10 and foreign matter derived by footpath.
According to structure as described above, when the impeller 10 of centrifugal pump 1 rotates, fluid is via inflow entrance 3 by suction inlet
19 guiding, be sucked into from suction inlet 19 along axis of rotation C in impeller 10, from exterior region 20 be directed to blade between stream
22, along the flow direction of the fluid of stream between blade 22 from the direction transformation along axis of rotation C be along the side of radial outside
To fluid flows out from hinder marginal part 21, is discharged from flow export 4 to outside.
In the present embodiment, blade 11 as shown in Fig. 2 the distance along the pressure face with blade 11 and blade 11 with
The equidistant imagining center line of suction surface, when exterior region 20 being set into 0 hinder marginal part 21 being set into 1, by the impeller 10
In the range of axis of rotation C is 0 to about 0.15 than θ/θ 1 as the angle of spread at center, the constant thickness of blade 11, the angle of spread
In the range of being about 0.15 to 0.3 than θ/θ 1 thickness of blade 11 has flex point, than θ/θ 1 is 0.3 to 0.7 in the angle of spread
In the range of, the thickness of blade 11 consistently reduces from the lateral side of hinder marginal part 21 of exterior region 20.Also, after the thickness of exterior region 20 is
3.3 times of the thickness of edge 21.In addition, the thickness t of exterior region 20 is preferably 0.1~0.3 times of the suction inlet of impeller 10.
In addition, as shown in figure 3, the exterior region 20 of blade 11 has fillet.In addition, the suction surface lateral pressure of hinder marginal part 21
Surface side is thinning.The thickness being made before fillet when the thickness tF of exterior region 20 is the design of exterior region 20, the thickness of hinder marginal part 21
Spend the thickness by suction surface lateral pressure surface side before thinning when tR is the design of hinder marginal part 21.
Fig. 4 represents the shape of the blade 11 of impeller 10 with three models.
In Fig. 4, transverse axis represents：As illustrated in fig. 2 in the distance along the pressure face with blade 11 and blade 11 with bearing
When exterior region 20 is set to 0 hinder marginal part 21 is set into 1 by the equidistant imagining center line of pressure surface, by the rotary shaft of the impeller 10
Heart C as center the angle of spread than θ/θ 1.The longitudinal axis is represented each angle of spread than the thickness t of θ/θ 1 blade divided by the trailing edge of blade
The thickness tR in portion and the value t/tR calculated.
In the range of the angle of spread is 0 to about 0.15 than θ/θ 1, the blade of model a impeller is constant, in angle of spread ratio
In the range of θ/θ 1 is about 0.15 to 0.3, the blade of model a impeller has flex point, is arrived in the angle of spread than θ/θ 1 for 0.3
In the range of 0.9, the blade of model a impeller is thinning with the ratio of constant from the lateral side of hinder marginal part 21 of exterior region 20.And
And the thickness of exterior region 20 is 4.9 times of the thickness of hinder marginal part 21.
In the range of the angle of spread is 0 to about 0.15 than θ/θ 1, the blade of model b impeller is constant, in angle of spread ratio
In the range of θ/θ 1 is about 0.15 to 0.3, the blade of model b impeller has flex point, is arrived in the angle of spread than θ/θ 1 for 0.3
In the range of 1.0, the blade of model b impeller is thinning with the ratio of constant from the lateral side of hinder marginal part 21 of exterior region 20.And
And the thickness of exterior region 20 is 3.3 times of the thickness of hinder marginal part 21.
In the range of the angle of spread is 0 to about 0.15 than θ/θ 1, the blade of model c impeller is constant, in angle of spread ratio
In the range of θ/θ 1 is about 0.15 to 0.3, the blade of model c impeller has flex point, is arrived in the angle of spread than θ/θ 1 for 0.3
In the range of 0.8, the blade of model c impeller is thinning with the ratio of constant from the lateral side of hinder marginal part 21 of exterior region 20.And
And the thickness of exterior region 20 is 2.2 times of the thickness of hinder marginal part 21.
The thickness relative to hinder marginal part 21 of the exterior region 20 of each impeller is gradual from model a to model c as described above
Ground is thinning.
These models a~c impeller tested on the actual measurement of the efficiency of pump.
In Figure 5, transverse axis represents wall thickness multiplying power m of the exterior region 20 relative to hinder marginal part 21, and the longitudinal axis represents efficiency of pump Δ %,
Read following result.
Can the perception model a efficiency of pump Δ % of impeller rise 1.5 percentages compared with the efficiency of pump Δ % of model c impeller
Point.
Can the perception model b efficiency of pump Δ % of impeller rise 2.3 percentages compared with the efficiency of pump Δ % of model c impeller
Point.
It is the hinder marginal part 21 of blade 11 in the thickness t of the blade 11 of the exterior region 20 of blade 11 it was found from result more than
More than 2.8 times and less than 5 times of thickness t of blade 11 when, efficiency of pump Δ % rises 1.5 compared with model c blade
It is more than percentage point.
Fig. 6 represents the shape of the exterior region of impeller with four models.
Each impeller has identical impeller outer diameter, identical blade piece number and identical pump casing shapes, only exterior region
Shape it is different.In figure 6, transverse axis represents that the side of wheel hub 13 of the blade 11 shown in Fig. 1 is set into 0 is set to 1.0 by the side of shield 15
When the width W from the side of wheel hub 13 of exterior region 20 to the side of the other end 14.The longitudinal axis represents the wheel hub from the exterior region 20 shown in Fig. 1
13 sides to the width position of the side of shield 15 radius r divided by the side of shield 15 radius ro and the value that calculates.
In exterior region, the blade of the impeller of model 1 is curved shape smooth as following：The radius ri of hub side is
About 0.63 times of the radius of shroud, the radius rm of pars intermedia are about 0.73 times of the radius of shroud.
In exterior region, the blade of the impeller of model 2 is curved shape smooth as following：The radius ri of hub side is
About 0.55 times of the radius of shroud, the radius rm of pars intermedia are about 0.65 times of the radius of shroud.
In exterior region, the blade of the impeller of model 3 is curved shape smooth as following：The radius ri of hub side is
About 0.46 times of the radius of shroud, the radius rm of pars intermedia are about 0.55 times of the radius of shroud.
In exterior region, the blade of the impeller of model 4 is curved shape smooth as following：The radius ri of hub side is
About 0.36 times of the radius of shroud, the radius rm of pars intermedia are about 0.52 times of the radius of shroud.
In addition, understand that above-mentioned each impeller is that little by little hub side is located opposite from relative to shroud from model 1 to model 4
The shape of radially inner side.
The impeller of these models 1~4 tested on the parsing of the efficiency of pump.
In figure 3, transverse axis represents each model, and the longitudinal axis represents efficiency of pump Δ %, reads following result.
Can the efficiency of impeller of perception model 2 rise 1.8 percentage points compared with the efficiency of the impeller of model 1.
Can the efficiency of impeller of perception model 3 rise 3.5 percentage points compared with the efficiency of the impeller of model 1.
Can the efficiency of impeller of perception model 4 rise 3.4 percentage points compared with the efficiency of the impeller of model 1.
It was found from result more than, the shape of the optimization model 2~4 of exterior region 20 of impeller 10.I.e., it is known that impeller 10 is preferred
, in the exterior region 20 of blade 11, the radius ri of the side of wheel hub 13 is 0.30~0.55 times of the radius ro of the side of shield 15, wheel hub
The radius rm of 13 sides and the pars intermedia of the side of shield 15 is 0.50~0.65 times of the radius ro of the side of shield 15.
As described above, in the exterior region 20 of blade 11, impeller 10 of the invention makes the side of wheel hub 13 of blade 11 compared to leaf
The side of shield 15 of piece 11 is located opposite from radially inner side, so as in the blade 11 as the radial position close to axis of rotation C
The side of wheel hub 13, the fluid for flowing into impeller 10 can be made to guide earlier to by blade 11, wheel hub 13 and shield 15 and surrounded and structure
Into blade between stream 22, therefore, with that will be flowed into the side of shield 15 of the blade 11 as the radial position away from axis of rotation C
Fluid to impeller 10 guides the situation to stream between blade 22 to compare, and the reduction of axle power can be made with same traffic, total head
The efficiency of pump is improved, and the effect for suppressing vibration can be improved.Because flow into the stream of impeller 10 in the exterior region 20 of blade 11
Body is swimmingly guided to stream 22 between blade, so being difficult to produce disorder in the flowing of fluid of shield 15 is connected on, is rubbed
Mistake of wearing is reduced, therefore can aid in the reduction of axle power.
In the exterior region 20 of blade 11, the radius ri of the side of wheel hub 13 is 0.30~0.55 times of the radius ro of the side of shield 15,
In exterior region 20, the radius rm of the side of wheel hub 13 and the pars intermedia of the side of shield 15 is the 0.50~0.65 of the radius ro of the side of shield 15
Times, on such blade 11, at least it is set as in exterior region 20 close to the side of wheel hub 13 and the side of shield 15 in suction surface 11n sides convex
Shape, concave shape is set as in pressure face 11p sides.That is, stream 22 is wide between being able to ensure that blade in pressure face 11p sides.
Blade 11 is at least set as smooth convex form in negative pressure surface side in exterior region 20 close to the side of wheel hub 13 and the side of shield 15,
So as to suppress to make to be sucked into the movement disorder of the fluid of impeller 10 while stream 22 between directing fluid to blade.
Approach the side of shield 15 of the exterior region 20 of suction inlet 19 and blade 11, so as to be sucked from suction inlet 19
Guide to stream 22 between blade smooth fluid.
Between the blade of centrifugal pump possessed impeller 10 in stream 22, on the basis of the main flow approximately along flow path
On, stripping of the two-dimensional current due to the barometric gradient in stream between blade 22 etc., vortex and flowing etc. is produced, this turns into efficiency
One of the reason for reduction.
Blade 11 is configured to relative to the side of wheel hub 13 be located in front of direction of rotation in the side of 20 shield of exterior region 15, so as to
Reducing turns into the generation of phenomenon the reason for reducing efficiency, therefore can improve efficiency.
In the hinder marginal part 21 of blade 11, when the side of wheel hub 13 and the side of shield 15 are in same position in a rotational direction, pass through
Fluid force caused by impeller 10 all acts on hinder marginal part 21, therefore produces flexure in blade 11, is produced by the flexure of blade 11
The disorder of the balance of raw direction of rotation, so as to which uneven radial load acts on bearing, turn into the original in the life-span for shortening bearing
Cause.
Blade 11 is configured to relative to the side of wheel hub 13 be located in front of direction of rotation in the side of 21 shield of hinder marginal part 15 of blade 11,
So that in the hinder marginal part 21 of blade 11, the rising of the static pressure of the side of wheel hub 13 can be suppressed, so flow out while smooth fluid can be made,
Therefore the generation of problem as described above can be suppressed.
When the piece number of blade 11 is more, the efficiency of pump improves, and still, because stream 22 narrows between blade, foreign matter is easy
Block.On the other hand, when blade 11 is a piece of, it can be ensured that stream 22 is wide between blade, but in the balance around axis of rotation C
Produce unbalanced, generation pulsation in discharge, efficiency of pump reduction due to this.Such as present embodiment, the piece number of blade 11 is set
Into two panels, so as to which stream 22 narrows compared with blade is a piece of situation between blade, but the logical of foreign matter is fully ensured on one side
The property crossed is while the balance around axis of rotation C is not produced unbalanced, therefore the efficiency of pump improves.
In the above-described embodiment, it is that the situation of so-called double shrouded wheel is illustrated to impeller.But such as Fig. 8
Shown, impeller 30 of the invention can also be the so-called unshrouded impeller for having blade 31 and wheel hub 33.
Impeller 30 does not have shield as double shrouded wheel, and impeller 30 is in blade 31 and the possessed of pump case 3 suction sleeve
There is small gap between 35 and rotate.Such impeller 30 is excellent in manufacture and handling ease this aspect compared with double shrouded wheel
It is different, if in addition, making great efforts research and discharge groove being located at into suction sleeve 35 etc., even if before the foreign matter of threadiness falls into blade 31
Edge 40, foreign matter are also easily drained via the discharge groove, thus such impeller 30 pass through in foreign matter it is excellent in property.
Even such impeller 30, in the exterior region 40 of blade 31, the radius ri of the preferably side of wheel hub 33 is suction sleeve
The radius rm of 0.30~0.55 times of the radius ro of 35 sides, the side of wheel hub 33 and the pars intermedia of suction sleeve 35 side is suction sleeve 35
0.50~0.65 times of the radius of side.Blade 31 is preferably, and sucks the radius ro of the side of sleeve 35 in exterior region 40 and suction covers
The radius rs of the suction inlet 39 of cylinder 35 is equal.It is configured to meet these conditions, so as to flow through by blade 31, wheel hub 33 and suction set
The energy loss of the fluid of stream 42 is reduced between the blade that cylinder 35 is formed, and can realize the high efficiency of pump.
As described above, in the impeller 30 of the present invention, in the exterior region 40 of blade 31, make the side of wheel hub 33 of blade 31 compared to
Being set as of blade 31 is located opposite from radially inner side across the side of suction sleeve 35 relative with wheel hub 33 of blade 31, so as to make
For close to the side of wheel hub 33 of the blade 31 of axis of rotation C radial position, the fluid that flow into impeller 30 can be drawn earlier
Be directed at by stream 42 between blade 31, wheel hub 33 and suction sleeve 35 blade that surrounds and form, thus with as away from rotation
The suction side of sleeve 35 of the blade 31 of axle center C radial position guides the fluid for flowing into impeller 30 to stream between blade 42
Situation is compared, and axle power can be made to reduce the efficiency of pump with same traffic, total head and improved, and can improve the effect for suppressing vibration
Fruit.
Because unshrouded impeller has gap between blade 31 and suction sleeve 35, leakage is produced from the gap.
Friction loss increase axle power rises when the leakage increases.But as described above, be configured to can in the side of wheel hub 33 of blade 31
The fluid for flowing into impeller 30 is guided to stream 42 between blade earlier, relatively reduced so as to suck the work(of the side of sleeve 35,
Therefore disorderly in the flowing of fluid to reduce, leakage is reduced.Because leakage is reduced, so as to identical total head, axle power
More flows are conveyed, therefore the efficiency of pump can be improved.
In addition, for the 30 unaccounted structure of impeller as unshrouded impeller and the impeller 10 as above-mentioned double shrouded wheel
It is identical.For example, in exterior region 40, the side of suction sleeve 35 of blade 31 is located in front of direction of rotation relative to the side of wheel hub 33, blade
31 at least laterally suck the side of sleeve 35 in exterior region 40 from wheel hub 33 is set as smooth convex form, pressure face in suction surface 31n sides
31p sides are set as smooth concave shape.
In addition, in the above description, the feelings to by the impeller 10,30 of the present invention being centrifugal pump possessed centrifugal impeller
Condition is illustrated as an example, and still, impeller of the invention is preferably applied to models of the specific rate Ns 100~1000 or so
The turbine pump enclosed.Therefore, impeller of the invention can also be diagonal pumps possessed diagonal impeller.
Above-mentioned embodiment is only one of the present invention, and according to the record, the present invention is not limited to this, the tool in each portion
Body structure being capable of appropriate design for change in the range of the action effect of the present invention is played.
Claims (15)
1. a kind of impeller, it is centrifugal pump or diagonal pumps possessed impeller, it is characterised in that
On the thickness of blade, the thickness of the exterior region of the blade is more than 2.8 times of the thickness of the hinder marginal part of the blade.
2. impeller according to claim 1, it is characterised in that
In the distance along the pressure face with the blade and the equidistant imagining center line with the suction surface of the blade
When the exterior region being set into 0 and the hinder marginal part being set into 1, in the angle of spread ratio using the axis of rotation of the impeller as center
In the range of 0 at least 0.1, the constant thickness of the blade.
3. impeller according to claim 2, it is characterised in that
In the distance along the pressure face with the blade and the equidistant imagining center line with the suction surface of the blade
When the exterior region being set into 0 and the hinder marginal part being set into 1, in the angle of spread ratio using the axis of rotation of the impeller as center
In the range of 0 to 0.2, the constant thickness of the blade.
4. the impeller according to claim 1 or 3, it is characterised in that
In the distance along the pressure face with the blade and the equidistant imagining center line with the suction surface of the blade
When the exterior region being set into 0 and the hinder marginal part being set into 1, in the angle of spread ratio using the axis of rotation of the impeller as center
In the range of 0.3 to 0.7, from the exterior region, laterally the hinder marginal part side consistently reduces the thickness of the blade.
5. the impeller according to any one of Claims 1-4, it is characterised in that
In the distance along the pressure face with the blade and the equidistant imagining center line with the suction surface of the blade
When the exterior region being set into 0 and the hinder marginal part being set into 1, in the angle of spread ratio using the axis of rotation of the impeller as center
In the range of 0.15 to 0.3, the thickness of the blade has flex point.
6. the impeller according to any one of claim 1 to 5, it is characterised in that
The thickness of the exterior region is 0.1~0.3 times of the diameter of the suction inlet of the impeller.
7. the impeller according to any one of claim 1 to 6, it is characterised in that
The impeller also has wheel hub and shield,
In the exterior region of the blade, the radius of the hub side of the blade be the radius of the shroud 0.30~
0.55 times.
8. the impeller according to any one of claim 1 to 7, it is characterised in that
The impeller also has wheel hub,
In the exterior region of the blade, the radius of the hub side of the blade be the radius for sucking sleeve side 0.30~
0.55 times, the suction sleeve is set as relative with the wheel hub across the blade.
9. the impeller according to claim 7 or 8, it is characterised in that
In the exterior region, the hub side and the pars intermedia of the shroud or the suction sleeve side of the blade
Radius is 0.50~0.65 times of the radius of the shroud or the suction sleeve side.
10. the impeller according to any one of claim 7 to 9, it is characterised in that
In the exterior region, laterally the shroud or the suction sleeve side are gradual from the wheel hub for the radius of the blade
Ground increases.
11. the impeller according to any one of claim 7 to 10, it is characterised in that
In the exterior region, the suction inlet of the radius and the impeller of the shroud of the blade or the suction sleeve side
Radius it is equal.
12. the impeller according to any one of claim 7 to 11, it is characterised in that
In the exterior region, the shroud of the blade or the suction sleeve side are located at rotation relative to the hub side
Turn in front of direction.
13. the impeller according to any one of claim 7 to 12, it is characterised in that
In the hinder marginal part of the blade, the shroud of the blade or the suction sleeve side are relative to the hub side
In front of direction of rotation.
14. the impeller according to any one of claim 7 to 13, it is characterised in that
Possesses blade described in two panels in the relative position of the axis of rotation across the impeller.
15. the impeller according to any one of claim 1 to 14, it is characterised in that
Foreign matter is by footpath in more than 76mm.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016110127A JP6758924B2 (en) | 2016-06-01 | 2016-06-01 | Impeller |
| JP2016-110127 | 2016-06-01 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN107448412A true CN107448412A (en) | 2017-12-08 |
Family
ID=60487056
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710399186.6A Pending CN107448412A (en) | 2016-06-01 | 2017-05-31 | Impeller |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6758924B2 (en) |
| CN (1) | CN107448412A (en) |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50403A (en) * | 1973-05-09 | 1975-01-07 | ||
| CN86210682U (en) * | 1986-12-29 | 1987-10-07 | 中国科学院工程热物理研究所 | Centrifugal pump |
| JPH09287593A (en) * | 1996-04-17 | 1997-11-04 | Kawamoto Seisakusho:Kk | Centrifugal pump and automatic water supply pump device using the same |
| JPH116496A (en) * | 1997-06-18 | 1999-01-12 | Ebara Corp | Impeller of sewage pump |
| CN1648463A (en) * | 2004-01-29 | 2005-08-03 | 三相电机株式会社 | Radial impeller |
| CN101096964A (en) * | 2006-06-26 | 2008-01-02 | 高其海 | Centrifugal type fluid machine blade wheel |
| CN103291653A (en) * | 2013-06-24 | 2013-09-11 | 江苏大学 | Low-specific-speed impeller and design method for blade thereof |
| CN204610367U (en) * | 2012-09-28 | 2015-09-02 | 新明和工业株式会社 | Centrifugal pump impeller and centrifugal pump |
| RU2579525C1 (en) * | 2015-02-02 | 2016-04-10 | Акционерное общество "Научно-производственная фирма "Невинтермаш" | Radial impeller grating of centrifugal stage |
| JP2016050486A (en) * | 2014-08-29 | 2016-04-11 | 株式会社日立製作所 | Fluid machinery and impeller of fluid machinery |
| WO2016067666A1 (en) * | 2014-10-27 | 2016-05-06 | 三菱重工業株式会社 | Impeller, centrifugal fluid machine, and fluid device |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57148087U (en) * | 1981-03-13 | 1982-09-17 | ||
| JPS61252893A (en) * | 1985-05-02 | 1986-11-10 | Hitachi Ltd | Sewage and waste pump |
| JPH0533793A (en) * | 1991-07-25 | 1993-02-09 | Fuji Electric Co Ltd | Mixed flow pump |
| JP3022845B2 (en) * | 1998-07-27 | 2000-03-21 | 株式会社三興ポンプ製作所 | Suction sand pump |
| CA2647689C (en) * | 2006-03-28 | 2015-07-07 | The Gorman-Rupp Company | Impeller |
| EP2711557B1 (en) * | 2012-09-20 | 2019-10-02 | Sulzer Management AG | An impeller for a centrifugal pump |
-
2016
- 2016-06-01 JP JP2016110127A patent/JP6758924B2/en active Active
-
2017
- 2017-05-31 CN CN201710399186.6A patent/CN107448412A/en active Pending
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50403A (en) * | 1973-05-09 | 1975-01-07 | ||
| CN86210682U (en) * | 1986-12-29 | 1987-10-07 | 中国科学院工程热物理研究所 | Centrifugal pump |
| JPH09287593A (en) * | 1996-04-17 | 1997-11-04 | Kawamoto Seisakusho:Kk | Centrifugal pump and automatic water supply pump device using the same |
| JPH116496A (en) * | 1997-06-18 | 1999-01-12 | Ebara Corp | Impeller of sewage pump |
| CN1648463A (en) * | 2004-01-29 | 2005-08-03 | 三相电机株式会社 | Radial impeller |
| CN101096964A (en) * | 2006-06-26 | 2008-01-02 | 高其海 | Centrifugal type fluid machine blade wheel |
| CN204610367U (en) * | 2012-09-28 | 2015-09-02 | 新明和工业株式会社 | Centrifugal pump impeller and centrifugal pump |
| CN103291653A (en) * | 2013-06-24 | 2013-09-11 | 江苏大学 | Low-specific-speed impeller and design method for blade thereof |
| JP2016050486A (en) * | 2014-08-29 | 2016-04-11 | 株式会社日立製作所 | Fluid machinery and impeller of fluid machinery |
| WO2016067666A1 (en) * | 2014-10-27 | 2016-05-06 | 三菱重工業株式会社 | Impeller, centrifugal fluid machine, and fluid device |
| RU2579525C1 (en) * | 2015-02-02 | 2016-04-10 | Акционерное общество "Научно-производственная фирма "Невинтермаш" | Radial impeller grating of centrifugal stage |
Non-Patent Citations (1)
| Title |
|---|
| 关醒凡: "《现代泵理论与设计》", 30 April 2011 * |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017214897A (en) | 2017-12-07 |
| JP6758924B2 (en) | 2020-09-23 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR101913147B1 (en) | Centrifugal impeller having backward blades using dual gradient sectional shape type | |
| CN105756991B (en) | A kind of double suction multiple flow passages impeller and its design method | |
| CN103375435A (en) | Pump suction pipe | |
| CN109915418A (en) | A kind of blade extension type vertical centrifugal pump airflow fence and the centrifugal pump using the airflow fence | |
| CN102947598A (en) | Compressor and turbomachine with optimized efficiency | |
| CN206636828U (en) | A kind of small size mixed-flow impeller | |
| CN106089808A (en) | A kind of blade diffuser with trailing edge structures before swallow-tail form and formative method thereof | |
| JP5314441B2 (en) | Centrifugal hydraulic machine | |
| CN105041719B (en) | A kind of double suction centrifugal pump guide-vane choma | |
| CN102889237B (en) | Blade wheel with large blades and small blades applying front edges with sharp corners and air compressor | |
| CN110500288B (en) | Vertical multistage pump space guide vane body | |
| CN202273867U (en) | Multi-stage partial emission pump | |
| CN102966591B (en) | Axial flow type fluid driving device | |
| CN102797697A (en) | Light and portable pump impeller | |
| CN107448412A (en) | Impeller | |
| CN106949087A (en) | Band back blade axle envelope formula core main pump impeller structure | |
| CN105370587A (en) | Compound molecular pump capable of reducing traction-level gap backflow | |
| CN107448413A (en) | Impeller | |
| CN211116664U (en) | Vertical multistage pump space guide vane body | |
| CN103994097A (en) | Double-suction impeller and double-suction vortex pump | |
| CN207961076U (en) | A kind of centrifugal pump structure using the double-deck guide vane blade | |
| CN103982441A (en) | Novel double-entry vortex pump | |
| CN203374491U (en) | Centrifugal pump with an inducer | |
| CN208185051U (en) | A kind of single-stage double-suction centrifugal pump impeller | |
| CN106812726A (en) | A kind of multistage centrifugal pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20171208 |