CN208123118U - A kind of centrifugal pump unshrouded impeller structure - Google PatentsA kind of centrifugal pump unshrouded impeller structure Download PDF
- Publication number
- CN208123118U CN208123118U CN201820537306.4U CN201820537306U CN208123118U CN 208123118 U CN208123118 U CN 208123118U CN 201820537306 U CN201820537306 U CN 201820537306U CN 208123118 U CN208123118 U CN 208123118U
- Prior art keywords
- vane plate
- groove structure
- centrifugal pump
- Prior art date
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- 230000037250 Clearance Effects 0.000 claims description 10
- 230000035512 clearance Effects 0.000 claims description 10
- 239000007788 liquid Substances 0.000 abstract description 7
- 239000012530 fluid Substances 0.000 description 18
- 238000010586 diagram Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000005119 centrifugation Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000006011 modification reaction Methods 0.000 description 1
- 230000002093 peripheral Effects 0.000 description 1
The utility model discloses a kind of centrifugal pump unshrouded impeller structures.Impeller includes the groove structure of vane plate, blade and blade edge, vane plate is disc-shaped, blade is circumferentially arranged and is fixed in blade plate end face, each blade is radially arranged along vane plate, each blade along the same side of vane plate circumferential direction is fixed with groove structure being located at, groove structure is parallel with blade, and groove structure is close to be fixed on the side of blade；A balance hole is provided on vane plate between adjacent blades, the utility model can increase gap flow resistance, reduces gap leakage flow rate, changes simultaneously local flow structure and leakage stream direction, it does not allow liquid stream directly to rush at next runner, reduces the impact that leakage stream flows impeller channel mainstream.
The utility model relates to a kind of impellers of pump, and in particular to a kind of centrifugal pump unshrouded impeller structure.
Centrifugal pump with open impellerpump is due to having the characteristics that pumped (conveying) medium flow is small, lift is high and is widely used.But it is high There is clearance leakage of blade tip stream and axial force in fast centrifugal pump unshrouded impeller.Both of these problems are affected to pump, especially It is that revolving speed is higher, influences more significant.
In the prior art, the design method of previous unshrouded impeller mostly uses the design method of double shrouded wheel, due to open type There is very big difference in impeller and double shrouded wheel structure, the type of flow of fluid is set in this way there is also very big difference The unshrouded impeller that meter comes out is unable to satisfy requirement.
Utility model content
The deficiencies of to overcome the prior art middle period to push up tip leakage flow, axial force balance, the utility model provides one kind Centrifugal pump unshrouded impeller structure can increase flow resistance, reduce the leakage stream at blade tip clearance, while being capable of providing support, increase Add rigidity.
The utility model adopts the following technical solution：
The impeller of the utility model is arranged between front shroud and back shroud, and impeller includes vane plate, blade and blade edge The groove structure of edge, vane plate is disc-shaped, and blade is circumferentially arranged and is fixed in blade plate end face, and each blade is along vane plate diameter To arrangement, for each blade positioned at groove structure is fixed with along the same side of vane plate circumferential direction, groove structure is parallel with blade, Groove structure is close to be fixed on the side of blade.
It is provided with balance hole on the vane plate, a balance hole, balance hole are provided on the vane plate between adjacent blades Including macropore and aperture, macropore and aperture are circumferentially alternately arranged along vane plate.
Pump chamber before being formed between the blade and front shroud, forms leaf between the intracavitary groove structure of front pump and front shroud Clearance flow between top.
Edge radical length of the groove structure length with blade close to front shroud side is equal, and along circumference of impeller Direction is evenly distributed.
The blade is circumferentially fixed in blade plate end face evenly and at intervals.
The groove structure makes rotating motion with pump shaft of centrifugal pump, increases gap flow resistance, reduces gap leakage flow rate, Changed simultaneously the local flow structure between blade and front shroud and leakage stream direction so that liquid stream do not rush at directly it is next Blade passage reduces impact of the fluid flowing to blade.
Axial force F suffered by back shroud medial surface when to be centrifuged pump work by the groove structure2Increase, balances Axial force F suffered by the back shroud lateral surface of part1。
It is made rotating motion by the groove structure and blade with the pump shaft of centrifugal pump, when fluid passes through groove structure, Fluid flow resistance increase is increased, to reduce the leakage rate at blade tip clearance stream.
The utility model has the beneficial effects that：
The utility model structure is simple, easy to process, overcomes the design method that traditional unshrouded impeller uses double shrouded wheel Deficiency.
The utility model is additionally arranged groove structure, increases projected area of the blade on back shroud, due to pressure be with Projected area is directly proportional, and projected area increase means that axial force increases on the inside of the increase of pressure, that is, back shroud, can portion Balance-dividing falls the axial force on the outside of back shroud.
It is recessed due to there is relative motion between groove structure and fluid when fluid passes through groove structure in the utility model Slot structure will receive the resistance of fluid, and the increase of flow resistance is so that energy is more consumed in the form of resistance, to reduce Leakage rate at blade tip clearance stream.
The utility model groove structure can change local flow structure and leakage stream direction, not allow liquid stream directly to rush at next A runner, so that smaller fluid flows the impact to blade.
Detailed description of the invention
Fig. 1 is the impeller tomograph of embodiment；
Fig. 2 is centrifugal pump stress diagram；
Fig. 3 is axial force of impeller schematic diagram；
Fig. 4 is a certain position cross-sectional view of blade.
Wherein：1, vane plate；2, blade；3, groove structure；4, front shroud；5, blade tip clearance stream；6, rear pump chamber；7, front pump Chamber, 8, balance hole.
With reference to the accompanying drawing and specific embodiment, the utility model is described in further detail, but this is practical new The protection scope of type is not limited to this.
As shown in Fig. 2, impeller is arranged between front shroud 4 and back shroud.As shown in Figure 1, impeller includes vane plate 1, leaf The groove structure 3 at 2 edge of piece 2 and blade, vane plate 1 is disc-shaped, and circumferentially arrangement is fixed on vane plate to blade 2 evenly and at intervals On 1 end face, each blade 2 is set along the radial arrangement of vane plate 1, each blade 2 positioned at along the circumferential the same side fixation of vane plate 1 Fluted structure 3, groove structure 3 is parallel with blade 2 (i.e. with radial parallel along vane plate 1), and the abutting of groove structure 3 is fixed on leaf The side of piece 2.Edge radical length of 3 length of groove structure with blade 2 close to 4 side of front shroud is equal, and along circumference of impeller Direction is evenly distributed.
The shaft core position of impeller is provided with axle sleeve, and axle sleeve is fixed on pump shaft, wherein blade inlet edge groove structure and blade It is integrated design, groove structure is positioned only at blade side therein, and the groove structure of each blade is arranged in the same side, The equal length of groove structure and blade, highly concordant with blade inlet edge, groove structure quantity is equal with the number of blade.
As shown in Figure 1, being provided with balance hole 8 on vane plate 1, a balance hole is provided on the vane plate 1 between adjacent blades 2 8, balance hole 8 includes macropore and aperture, and macropore and aperture are alternately arranged along vane plate 1 is circumferential, i.e. circumferentially first of sequence The balance hole 8 of a macropore is provided on vane plate 1 between blade 2 and second blade 2, then circumferentially second of sequence The balance hole 8 of an aperture is provided on vane plate 1 between blade 2 and third blade 2.Two kinds of vane plate are various sizes of Hole is arranged and is mainly used for balancing axial thrust at the vane plate of macropore, and leaf can be reinforced with support blade by arranging at the vane plate of aperture Take turns rigidity.
It is as follows that principle is embodied in the utility model：
As shown in Fig. 2, pump chamber 6 after being formed between vane plate 1 and back shroud, blade 2 is with before in the structure of original centrifugal pump Pump chamber 7 before being formed between cover board 4 forms blade tip clearance stream 5 between preceding 7 indent slot structure 3 of pump chamber and front shroud 4.
In centrifugal pump, liquid is in low pressure P1Under from import enter impeller, and in High Voltage P2Lower outflow impeller is to out Mouthful, P1Indicate impeller inlet pressure, P2Indicate impeller outlet pressure.The outlet pressure of centrifugal pump is greater than inlet pressure, and has leaf Sheet 1 causes impeller front and back asymmetric without the blade wheel structure of front shroud, so that impeller axial ends stress, and suffered liquid pressure Power is unequal, and generates axial thrust.
As shown in Fig. 2, the pressure that impeller outlet side generates and is applied to vane plate lateral surface isImpeller eye Side generates and the pressure that is applied to vane plate medial surface isPressure difference is Due to P2>P1, so △ P is positive value, therefore this pressure difference is formed axial force when centrifugal pump operating, specially one along leaf Wheel shaft to and by outlet be directed toward entrance power.In formula, PrAxial pressure suffered by-vane plate lateral surface, PlOn the inside of-vane plate Axial pressure, P suffered by face1- impeller inlet pressure, P2- impeller outlet pressure, R2- impeller outlet radius, Rm- impeller into Port radius, △ P-impeller two sides pressure difference.
Being greater than inlet pressure by the outlet pressure of centrifugal pump is influenced, this pressure difference is just making leaf when centrifugal pump operates Wheel/blade board ends form axial force, and as shown in Fig. 3 (b), two axial forces resultant forces are one along impeller axial direction and by exporting It is directed toward the power of entrance, the utility model balances two axial forces by the setting of groove structure, so that resultant force weakens.
As shown in figure 3, axial force suffered by 1 lateral surface of vane plate (i.e. the pressure of impeller outlet side generation) uses following public affairs Formula calculates, and 1 lateral surface of vane plate is the one side of the not set blade of vane plate 1：
In formula, F1Axial force suffered by-back shroud lateral surface, P2- impeller outlet pressure, R2- impeller outlet radius, Rh- impeller hub radius, RaThe macropore radius of-balance hole, RbThe aperture radius of-balance hole, z1Balance hole on-vane plate Big hole number, z2The small hole number of balance hole on-vane plate, ρ-fluid density, g-acceleration of gravity, Hp- impeller goes out Mouth gesture lift, H1- impeller single-stage lift, u2The peripheral speed of-impeller outlet, ω-impeller angular velocity of rotation.Part of ruler Very little such as Fig. 3 (a) is shown.
Axial force suffered by 1 medial surface of vane plate (i.e. the pressure of impeller eye side generation) is calculated using the following equation, leaf 1 medial surface of sheet is that vaned one side is arranged in vane plate 1：
In formula, F2Axial force suffered by-vane plate medial surface, Rm- impeller inlet radius, b-groove structure width, θ- Blade pitch angle.
After groove structure 3 is set, projected area of the blade 2 on vane plate 1 is increased, since pressure is and projected area Directly proportional, projected area increase means the increase of pressure, so that axial force suffered by 1 medial surface of vane plate when centrifugation pump work F2Increase, balances axial force F suffered by 1 lateral surface of partial blade plate1.Although can not complete equipilibrium fall the axis in the outside of vane plate 1 Xiang Li, but the range that can be balanced is 70%-85%, i.e. F2=(70%~85%) F1。
In addition, the blade tip clearance stream 5 in original centrifugal pump structure, between preceding 7 indent slot structure 3 of pump chamber and front shroud 4 Place, as shown in Fig. 4 (a), the setting of groove structure is not so that rush at next blade 2 directly by the liquid stream of blade.
And after the utility model adds groove structure 3, groove structure 3 and blade 2 make rotating motion with the pump shaft of centrifugal pump, When fluid passes through groove structure 3, due to there is relative motion between groove structure 3 and fluid, groove structure 3 can generate fluid New resistance, new drag direction and groove structure 3 relative to fluid directional velocity on the contrary, its sizeIncrease Add fluid flow resistance, as shown in Fig. 4 (b), changes local flow structure and the leakage stream between blade 2 and front shroud 4 Direction, so that liquid stream does not rush at next blade 2 directly, so that fluid energy is more consumed in the form of resistance, to reduce Leakage rate at blade tip clearance stream 5 reduces fluid and flows impact to blade 2.
In new resistance calculation formulae：FD- flow resistance, CD- dimensionless flow resistance coefficient, ρ-fluid density, V- Fluid speed of incoming flow, A-groove structure effective cross section product, projected area of the groove structure (3) on vane plate (1).
The embodiment is the preferred embodiment of the utility model, but the utility model is not limited to above-mentioned embodiment party Formula, without departing substantially from the substantive content of the utility model, those skilled in the art can be made any apparent Improvement, replacement or modification belong to the protection scope of the utility model.
1. a kind of centrifugal pump unshrouded impeller structure, impeller is arranged between front shroud (4) and back shroud, it is characterised in that：Impeller Groove structure (3) including vane plate (1), blade (2) and blade (2) edge, vane plate (1) is disc-shaped, and blade (2) is circumferentially Arrangement is fixed on vane plate (1) end face, and each blade (2) is radially arranged along vane plate (1), and each blade (2) is being located at edge The same side of vane plate (1) circumferential direction is fixed with groove structure (3), and groove structure (3) is parallel with blade (2), groove structure (3) It is close to be fixed on the side of blade (2).
2. a kind of centrifugal pump unshrouded impeller structure according to claim 1, it is characterised in that：On the vane plate (1) It is provided with balance hole (8), a balance hole (8) is provided on the vane plate (1) between adjacent blades (2), balance hole (8) includes macropore And aperture, macropore and aperture are circumferentially alternately arranged along vane plate (1).
3. a kind of centrifugal pump unshrouded impeller structure according to claim 1, it is characterised in that：
Pump chamber (7) before being formed between the blade (2) and front shroud (4), in preceding pump chamber (7) indent slot structure (3) and front cover Blade tip clearance stream (5) are formed between plate (4).
4. a kind of centrifugal pump unshrouded impeller structure according to claim 1, it is characterised in that：
Groove structure (3) length is equal close to the edge radical length of front shroud (4) side with blade (2), and along leaf It is evenly distributed to take turns circumferencial direction.
5. a kind of centrifugal pump unshrouded impeller structure according to claim 1, it is characterised in that：
The blade (2) is circumferentially fixed on evenly and at intervals on vane plate (1) end face.
Priority Applications (1)
|Application Number||Priority Date||Filing Date||Title|
|CN201820537306.4U CN208123118U (en)||2018-04-16||2018-04-16||A kind of centrifugal pump unshrouded impeller structure|
Applications Claiming Priority (1)
|Application Number||Priority Date||Filing Date||Title|
|CN201820537306.4U CN208123118U (en)||2018-04-16||2018-04-16||A kind of centrifugal pump unshrouded impeller structure|
|Publication Number||Publication Date|
|CN208123118U true CN208123118U (en)||2018-11-20|
Family Applications (1)
|Application Number||Title||Priority Date||Filing Date|
|CN201820537306.4U Active CN208123118U (en)||2018-04-16||2018-04-16||A kind of centrifugal pump unshrouded impeller structure|
Country Status (1)
|CN (1)||CN208123118U (en)|
- 2018-04-16 CN CN201820537306.4U patent/CN208123118U/en active Active
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