CN102667176B - Centrifugal pump - Google Patents
Centrifugal pump Download PDFInfo
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- CN102667176B CN102667176B CN201080053381.XA CN201080053381A CN102667176B CN 102667176 B CN102667176 B CN 102667176B CN 201080053381 A CN201080053381 A CN 201080053381A CN 102667176 B CN102667176 B CN 102667176B
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- impeller
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- convex shaped
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The convex shaped part (62) of shell (51), the speed composition of radial direction of impeller will be accompanied by by current, be the summit (623) passed through of radial direction flow velocity and with the orthogonal straight line of the axis of rotation (X) of impeller (53) as the first baseline (L1), axis of rotation direction from the first baseline (L1) along impeller (53) is separated to the position of predetermined distance (h) to impeller side, with the orthogonal plane of the axis of rotation of impeller (53) as datum level (α), will be by the intersection of datum level (α) and the inner peripheral surface (624) of convex shaped part (62) and the line parallel with the axis of rotation (X) of impeller (53) in the situation as the second baseline (L2), from aforementioned summit (623) to the first baseline (L1) with the distance (Lx) of the intersection point of the second baseline (L2), around the axis of rotation of impeller (53), the radial direction flow velocity (V) of current becomes the afore-mentioned distance (Lxa) that maximum radial direction flow velocity maximum position (A) is located, than becoming at radial direction flow velocity, the afore-mentioned distance (Lxb) that minimum radial direction flow velocity minimum position (B) locates is large.
Description
Technical field
The present invention relates to centrifugal pump, particularly, relate to the shell mechanism of centrifugal pump.
Background technology
Past, as a kind of dual suction type centrifugal pump in this centrifugal pump, as shown in figure 13,Be equipped with shell 1 and be arranged on the impeller 3 on main shaft 2. Shell 1 has: at impeller 3In axis of rotation direction, be positioned at impeller 3 side volute suction passage 11 and around leafThe discharge stream 12 that the axis of rotation of wheel 3 forms. Impeller 3 is stream 13 in inside has impeller,Stream 13 utilizes towards the suction oral area 14 of axis of rotation direction opening and shell 1 in impellerSuction passage 11 is communicated with, and, utilize towards with the orthogonal radial direction opening of axis of rotationDischarging oral area 15 is communicated with the discharge stream 12 of shell 1.
Under the state rotating around axis of rotation by the driving of main shaft 2 at impeller 3, flow intoThe water of the suction passage 11 of shell 1, rotates one on one side along the spiral type of suction passage 11The suction oral area 14 that impeller 3 is passed through from the terminal part towards impeller of suction passage 11 in limit is to leafIn wheel, stream 13 flows into. The water that flows into stream 13 in impeller is subject to being produced by the rotation of impeller 3Centrifugal force, be ejected into the discharge stream 12 of shell 1 from discharging oral area 15. As existing skillArt document, known Japanese Patent Publication communique (Unexamined Patent 3-290096 communique and JP61-49195 communique).
Summary of the invention
Invent problem to be solved
In said structure, when the current that rotate in the suction passage 11 at shell 1 are from inlet flowWhen the terminal part towards impeller on road 11 flows into the suction oral area 14 of impeller 3, as Figure 13Shown in middle arrow, rotate up in the side of the axis of rotation along impeller 3.
Sharply turning to of these current produces peeling off of current, and the loss of flood peak is increased. Due to headThe increase of loss has strengthened pressure drop, so, cause the suction causing due to the generation in holeEnter the reduction of performance. When occurring when hole, cause the sending out of reduction, vibration and noise of pump performanceHarmful phenomenons such as life, burn into damage.
Therefore, in first prior art document, the suction oral area that current direction impeller is flowed intoFormation is similar to bell-mouthed shape, sucks oral area outstanding from the inner surface of shell, at suction inletThe slot part of annular or arc between portion and inner surface of outer cover, is equipped with, with the orthogonal side of pump shaftUpwards mobile current enter and suck the slot part of oral area, not only its flow velocity are reduced but also by slot partCurrent inducing action makes to rotate composition and becomes large, and whereby, current rotate while cross suction inletPortion, to the direction travel direction conversion parallel with pump shaft.
In second prior art document, in dual suction type centrifugal pump, towards the suction of impellerThe whole circumferential part cross sectional shape of inlet portion forms in the following manner, that is, to suck oral areaUnder the state of rotation, from the upstream side starting point of the current that are inhaled into towards downstream terminal, curved surfaceRadius of curvature and impeller end face and curved surface summit between interval diminish gradually, upstream side risesThe current of point, because the radius of curvature of curved surface is larger than the radius of curvature of the curved surface in other downstream,So change along curved surface travel direction.
The object of the application's invention is to provide a kind of centrifugal pump, tries hard to be produced by pump becomingThe shell shape of the main cause of noise, become the obstruction of pump suction performance main cause outsideHull shape shape improves.
Solve the scheme of problem
In order to solve above-mentioned problem, centrifugal pump of the present invention, is characterized in that, around rotating shaftThe impeller of heart rotation has stream and the blade being configured in the interior stream of impeller in impeller, in impellerStream have to the suction oral area of the axis of rotation direction opening of impeller and to impeller radially sideTo the discharge oral area of opening, have around the shell of impeller: in the axis of rotation direction of impellerThe volute suction passage that is positioned at the side of impeller and be communicated with the suction oral area of impeller and enclosingThe discharge stream that forms and be communicated with the discharge oral area of impeller around the axis of rotation of impeller, is suckingThe position being around connected with the edge of opening of the suction oral area of stream in impeller in the internal face of streamForm to the convex shaped part of the axis of rotation direction protuberance of impeller, this convex shaped part, will pass through currentBe accompanied by the speed composition of the radial direction of impeller, summit that radial direction flow velocity passes through and withThe orthogonal straight line of the axis of rotation of impeller is as the first baseline, will be from the first baseline along impellerAxis of rotation direction separate the position of predetermined distance h and the axis of rotation of impeller to impeller sideOrthogonal plane is as datum level, by the intersection of the inner peripheral surface by datum level and convex shaped part and withIn the situation of the parallel line of the axis of rotation of impeller as the second baseline, from aforementioned summit to theIn the distance L x of the intersection point of one baseline and the second baseline, around the axis of rotation of impeller, waterThe radial direction flow velocity of stream becomes the afore-mentioned distance at maximum radial direction flow velocity maximum position placeLxa, than become the aforementioned of minimum radial direction flow velocity minimum position place at radial direction flow velocityDistance L xb is large.
Centrifugal pump of the present invention, is characterized in that, has leaf around the impeller of axis of rotation rotationStream and the blade being configured in the interior stream of impeller in wheel, in impeller, stream has revolving to impellerTurn the suction oral area of axis direction opening and the discharge oral area to the radial direction opening of impeller,Shell around impeller has: in the axis of rotation direction of impeller, be positioned at the side of impeller and withThe volute suction passage that the suction oral area of impeller is communicated with and around the rotating shaft heart of impellerThe discharge stream that the discharge oral area of Cheng Bingyu impeller is communicated with, in the internal face of suction passage with leafIn wheel, around the edge of opening of the suction oral area of stream, connected position forms the rotating shaft to impellerThe convex shaped part of heart direction protuberance, this convex shaped part forms the shape meeting the following conditions, described conditionFor: with the blade initiating terminal position in stream in impeller till the rotation on the summit of convex shaped partThe distance of axis direction is B, with in the axis of rotation direction of impeller from stream in impellerBlade initiating terminal position to the suction passage of the volute shell of the suction oral area subtend of impellerInternal face in highest distance position till distance be A, B/A is 0.23 to 0.31.
In addition, in centrifugal pump of the present invention, it is characterized in that, convex shaped part from the first baselineTill along the distance H of the edge of opening of the suction oral area of the axis of rotation direction of impeller,The surrounding of the axis of rotation of impeller is constant.
In addition, in centrifugal pump of the present invention, it is characterized in that, convex shaped part comprising radiusDirection flow velocity maximum position is in interior afore-mentioned distance in the predetermined distance scope of circumferential directionLxa is larger than the afore-mentioned distance Lxb at radial direction flow velocity minimum position place.
In addition, in centrifugal pump of the present invention, it is characterized in that, the inner peripheral surface of convex shaped part formsThe curved surface of the convex changing smoothly towards the axis of rotation side of impeller.
In addition, in centrifugal pump of the present invention, it is characterized in that, the inner peripheral surface of convex shaped part formsThe curved surface changing smoothly along circumferential direction.
In addition, in centrifugal pump of the present invention, it is characterized in that, the inner peripheral surface of convex shaped part formsThe curved surface of the convex changing smoothly with circular arc towards the axis of rotation side of impeller, from radius sideTo flow velocity maximum position till in circumferential direction the position of 120 °, afore-mentioned distance Lx is than halfThe afore-mentioned distance Lxb at direction flow velocity minimum position place, footpath is large.
In addition, in centrifugal pump of the present invention, it is characterized in that, it is 0.25 that formation meets B/AThe shape of the condition to 0.29.
In addition, in centrifugal pump of the present invention, it is characterized in that, convex shaped part is to be independent of shellThe removable convex shaped part forming.
In addition, in centrifugal pump of the present invention, it is characterized in that, convex shaped part and shell are oneBe shaped.
In addition, in centrifugal pump of the present invention, it is characterized in that, convex shaped part is by annular construction memberForm, and be arranged on shell.
In addition, in centrifugal pump of the present invention, it is characterized in that, described centrifugal pump is at impellerThe dual suction type centrifugal pump of the chlamydate suction passage of both sides tool of axis of rotation direction.
The effect of invention
According to the present invention, by making the radial direction flow velocity in the axis of rotation ambient water of impellerThe distance L xa that becomes maximum radial direction flow velocity maximum position becomes than radial direction flow velocityThe distance L xb of little radial direction flow velocity minimum position is large, can be suppressed at current rotation on one sideCross convex shaped part on one side produces in the time that the direction travel direction parallel with the axis of rotation of impeller changedThe peeling off of current, can suppress the generation of the noise causing due to the generation in hole. In addition,By on the internal face of the suction passage of shell with impeller in the opening edge of suction oral area of streamEdge around connected position has to the convex shaped part of the axis of rotation direction protuberance of impeller, Ke YihuanThe current that sharply turn to, improve pump suction performance.
Brief description of the drawings
Fig. 1 is the perspective view that represents the major part of the centrifugal pump in embodiments of the invention 1.
Fig. 2 (a) is the cutaway view of the A part of Fig. 1, is (b) the cuing open of B part of Fig. 1View.
Fig. 3 is the cutaway view that represents the centrifugal pump in embodiment 1.
Fig. 4 is the ideograph that represents the radial direction velocity flow profile of resolving.
Fig. 5 is the curve map that represents the circumferencial direction distribution of radial direction flow velocity.
Fig. 6 is the curve map that represents the circumferencial direction distribution of radial direction flow velocity.
Fig. 7 is the front view that represents the centrifugal pump in embodiment 1.
Fig. 8 is the top view that represents the connection of the centrifugal pump in embodiment 1.
Fig. 9 is the improved curve map that represents noise.
Figure 10 is the cutaway view of the centrifugal pump in embodiments of the invention 2.
Figure 11 represents the B/A of the centrifugal pump in embodiment 2 and falling of expression intake performanceThe curve map of the relation of suction specific rate S3% when low 3% lift.
Figure 12 is the pass that is illustrated in B/A and the highest efficiency eta max of the centrifugal pump in embodiment 2The curve map of system.
Figure 13 is the cutaway view that represents the centrifugal pump of prior art.
Detailed description of the invention
Embodiment 1
Embodiments of the invention 1 are described with reference to the accompanying drawings below. In Fig. 3, dual suction type fromHeart pump is equipped with the impeller 53 being driven by main shaft 52 in the inside of shell 51. Shell 51 hasIn the axis of rotation direction of impeller 53, be positioned at the volute suction passage of the side of impeller 5354, and there is the discharge stream 55 forming around the axis of rotation of impeller 53.
In addition, as shown in Figure 4, when the straight line to connect rotating shaft center and tongue 511 as0 °, while representing the anglec of rotation of flow direction of current 622 by vortex angle θ, suction passage54 form from 0 ° to 360 ° of the specific anglec of rotation, the axis of rotation side of the tongue 511 of shell 51To and the shape of the narrowed width of radial direction.
Impeller 53 has stream 58 in impeller between wheel hub 56 and guard shield 57, at wheel hub 56Form multiple blades 59 with the assigned position of guard shield 57. In impeller, stream 58 utilizes towards impeller53 the suction oral area 60 of axis of rotation direction opening and the suction passage 54 of shell 51 are communicated with,And, utilize towards with the discharge oral area of the orthogonal radial direction opening of the axis of rotation of impeller 5361 are communicated with the discharge stream 55 of shell 51. Blade 59 joins wheel hub 56 and guard shield 57 toUpper, extend to the terminal location of discharging oral area 61 places from sucking the initiating terminal position of oral area 60.
In the internal face of suction passage 54 with impeller in the opening of suction oral area 60 of stream 58Edge is connected position around, and shell 51 has protruding along the surrounding of the axis of rotation of impeller 53Shape portion 62, convex shaped part 62 can be integrally formed in the time of cast casing 51, also can with shell 51Separately form independently and form replaceably.
Convex shaped part 62 forms the shape meeting the following conditions. , as shown in Figures 1 and 2, protrudingShape portion 62 swells in the axis of rotation direction of impeller 53, and current 622 are accompanied by formation impellerThe radial direction flow velocity of the speed composition of 53 radial direction is by its top 621, in the face of suckingOral area 60, the inner peripheral surface 624 from summit 623 to edge of opening 601 forms towards impeller 53Axis of rotation side with conic section (parts for circle, ellipse, parabola, hyperbola etc.)The curved surface of the convex that shape changes smoothly.
And, for convex shaped part 62, by from its summit 623 to the rotating shaft of impeller 53The line that the orthogonal direction of heart X is extended is as the first baseline L1, will from the first baseline L1In the axis of rotation direction of impeller 53, separate the position of predetermined distance h and the rotation of impeller 53The orthogonal plane of axle center X, will be by the interior week of datum level α and convex shaped part 62 as datum level αThe intersection 625 of face 624 and the line parallel with the axis of rotation X of impeller 53 are as the second baselineL2, will be from summit 623 along the first baseline L1 until the first baseline L1 and the second baseline L2Situation as Lx of the distance of intersection point under, according to around the axis of rotation at impeller 53, waterThe radial direction flow velocity of stream 622 becomes the distance at maximum radial direction flow velocity maximum position A placeLxa becomes the distance at minimum radial direction flow velocity minimum position B place than radial direction flow velocityThe mode that Lxb is large, changes the inner peripheral surface formation of convex shaped part 62 smoothly along circumferential directionCurved surface.
In addition, the axis of rotation direction from the first baseline L1 along impeller 53 of convex shaped part 62Till suck the distance H of the edge of opening 601 of oral area 60, at the axis of rotation of impeller 53Around constant. In the present embodiment, from radial direction flow velocity maximum position A along circumferentiallyThe distance L x at the interval La of the predetermined distance of direction place, than at radial direction flow velocity minimum position BThe distance L xb at place is large, and still, the length of the interval La of predetermined distance can be set arbitrarily, rightIn this point, will be described later.
In said structure, revolve around axis of rotation by the driving of main shaft 52 at impeller 53Under the state turning, flow into the water of the suction passage 54 of shell 51, on one side along suction passage 54Spiral type rotation, on one side from the terminal part of suction passage 54 by the suction oral area of impeller 5360 flow into stream 58 in impeller. The water flowing into stream 58 in impeller, is subject to by impeller 53Rotation produce centrifugal force, from discharge oral area 61 spray to the discharge stream 55 of shell 51.
In the suction passage 54 of shell 51 rotation current 622, from suction passage 54 toWhen the suction oral area 60 of impeller 53 flows into, along the rotating shaft of the axis of rotation X of impeller 53The directional steering of heart X. At this moment, be accompanied by the current 622 of radial direction flow velocity, cross alongThe convex shaped part 62 that the axis of rotation of impeller 53 around forms, makes to axis of rotation direction anxious wherebyCurrent that play turns to, particularly slow down along the current of shell 51, suppress current from shell 51Peel off, thereby, can suppress the generation in hole, to suppress the generation of noise. And then,Can suppress due to the reduction of the reduction that the pump suction performance that causes of hole occurs, pump performance,The generation of vibration, burn into damage.
To be described in detail below. Fig. 4 is the current 622 that represent in centrifugal pump of the present inventionMobile ideograph, Fig. 5 be the anglec of rotation θ, the distance L x that represent suction passage 54 withAnd the curve map of the relation of radial direction flow velocity V. Distance L x(dimensionless), be by impellerThe value of the distance L x of 53 axis of rotation each anglec of rotation is around divided by making distance L xThe nothing that the standard value of distance L x constant in the whole length of convex shaped part 62 obtainsThe value of dimension. Radial direction flow velocity V(dimensionless), be by the axis of rotation week of impeller 53The dimensionless that the value of the radial direction flow velocity V of each anglec of rotation of enclosing obtains divided by mean flow rateThe value of changing, and mean flow rate is that pump soakage is obtained divided by the area that sucks oral area 60.
In Fig. 5, track K1 represents to make distance L x permanent in the whole length of convex shaped part 62The situation of fixed reference example, under this condition, utilizes track K2 to be illustrated in revolving of impeller 53The radial direction flow velocity V of the rotating shaft heart each anglec of rotation around.
Track K3 is the track relevant to the present embodiment, situation about being expressed as follows, that is: fromRadial direction flow velocity maximum position A is along the interval La of predetermined distance of circumferential direction, from rotationIn the scope that angle is 0 ° to 90 °, distance L x is than the distance at radial direction flow velocity minimum position B placeLarge from Lxb, and make accordingly distance with the radial direction flow velocity V in each anglec of rotationLx reduces gradually, as shown in track K4, can be also at the model from 0 ° to 120 ° of the anglec of rotationIn enclosing, distance L x than the distance L xb at radial direction flow velocity minimum position B place large and withThe condition that the radial direction flow velocity V of each anglec of rotation makes distance L x reduce gradually accordingly.Under the condition of track K3, around each of the axis of rotation that is illustrated in impeller 53 with track K5The radial direction flow velocity V of the individual anglec of rotation. In addition, in track K4, radial direction flow velocityV is substantially identical with the situation in track K5.
As can be as seen from Figure 5, in the present embodiment, radial direction flow velocity maximumPosition A, in the scope from 0 ° to 30 ° of the anglec of rotation, from radial direction flow velocity dominant bitPut A along the interval La of predetermined distance of circumferential direction, in the scope of 0 ° to 90 ° of the anglec of rotation,Or in the scope (region) of 0 ° to 120 ° of the anglec of rotation, distance L x compares radial directionThe distance L xb at flow velocity minimum position B place is large, whereby, and half of the current 622 in the present embodimentFootpath direction flow velocity V(K5) become than the radial direction flow velocity V(K2 in the situation of reference example)Little, as shown in table 1, compare with reference example, in the present embodiment, expression is peeled off, holeSituation negative pressure condition reduce.
[table 1]
From convex shaped part top, on inner peripheral surface, there is the situation in negative pressure (hole)
As a result, rotate at current 622 while cross convex shaped part 62 and to impeller 53When the parallel direction travel direction of axis of rotation X is changed, can suppress due to inhomogeneous inflowAnd peeling off of the current 622 of the region generating accelerating at flow velocity can suppress the generation in hole,To suppress the generation of noise. And then, peel off by can suppress, can suppress intake performanceThe reduction of reduction, pump performance, the generation of vibration, burn into damage.
As shown in Figure 6, setpoint distance Lx becomes than radial direction flow velocity minimum bit arbitrarilyThe large scope of distance L xb of putting B place, the structure of situation described below etc. is all possible,That is: the situation (track that in the scope from 0 ° to 90 ° of the anglec of rotation, distance L x is reduced graduallyK6); In the scope from 0 ° to 90 ° of the anglec of rotation by distance L x keep constant after, fromThe situation (track K7) that makes it to reduce gradually in the scope that the anglec of rotation is 90 ° to 210 °; FromIn the scope that the anglec of rotation is 0 ° to 90 °, distance L x is kept constant after, from the anglec of rotationThe situation (track K8) that makes it to reduce gradually in the scope of 90 ° to 300 °; From the anglec of rotationThe situation (K9) that makes distance L x reduce gradually in the scope of 0 ° to 300 °; From the anglec of rotationIn the scope of 0 ° to 300 °, make distance L x be the situation (track that conic section ground reduces graduallyK10）。
In addition, in Fig. 5, the radial direction flow velocity V 0 ° time declines, and is due to tongue 511Shape radial direction composition reduced or the frictional resistance increase of shell causes. EnterAnd, in Fig. 5, Fig. 6, why only the anglec of rotation is described to 300 °, be because,In the present embodiment, in the time exceeding 300 °, the top 621 of convex shaped part contacts with shell 51 and quiltAbsorb, become indefinite.
In Fig. 9, represent, utilizing as shown in Figures 7 and 8 hookup 801 by centrifugal pump 800Be connected under the condition using on motor 802 four positions around centrifugal pump 800The variation of the noise that D1～D4 place measures.
Fig. 9 is expressed as follows the poor of described noise at four D1～D4 places that locate, that is,Represent to make distance L x making an uproar constant reference example in the whole length of convex shaped part 62Sound, and as in this embodiment, comprise radial direction flow velocity maximum position A interior alongThe interval La of the predetermined distance of circumferential direction, in the scope of 0 ° to 90 ° of the anglec of rotation, distanceLx is poorer than the noise in the large situation of the distance L xb at radial direction flow velocity minimum position B place.As shown in Figure 9, even if the discharge rate of pump is changed, the D1 that locates at four positions～The noise of the present invention at D4 place is also in than the low scope of the noise of reference example.
In the present embodiment, by making distance H constant, the shape of convex shaped part becomes simply, systemBecome easily, can seek to reduce costs.
And then, by so that comprise radial direction flow velocity maximum position interior along circumferential directionPredetermined distance within the scope of distance L x than the distance L xb at radial direction flow velocity minimum position placeLarge mode forms convex shaped part, produces soon the high rule of possibility of peeling off at radial direction flow velocityWithin the scope of set a distance, can suppress to peel off, can more effectively suppress the generation of noise.
Particularly, preferably, from the scope of 0 ° to 120 ° of the anglec of rotation, radial direction velocity ratioMean flow rate is fast, using this scope as predetermined distance scope. More preferably, radial direction is flowedShort-term training be 1.4 times of mean flow rate above 0 ° to 90 ° as predetermined distance scope.
In addition, also can set predetermined distance scope from 0 ° to 360 ° of the anglec of rotation, still,In the present embodiment, in the anglec of rotation, from 0 ° to 90 ° in the situation that, shell weight increases by 1%. SeparatelyOn the one hand, when the anglec of rotation is during from 0 ° to 360 °, shell weight increases by 4%, with the anglec of rotationCompare from the situation of 0 ° to 90 °, the increase of weight reaches 4 times. If consider cost, in effectLarge the carrying out in the scope of 0 ° to 90 ° of the anglec of rotation of fruit is more effective.
And then, in the present embodiment, be level and smooth curved surface by making the inner peripheral surface of convex shaped part, waterStream is difficult to produce variation sharply on inner peripheral surface, can more suppress to peel off.
In the present embodiment, convex shaped part 62 is integrally formed in the time of cast casing 51, still, and distanceBecome than the large position of distance L xb at radial direction flow velocity minimum position B place from Lx, also canTo separate and to form independently and can change with shell 51. By changing,In the situation that convex shaped part 62 damages, needn't change shell 51, just can by changing convex shaped part 62With easily by pump reparation, and, at noise or vibration, intake performance due to operating conditionIn situation about changing and worsen. By changing convex shaped part 62, can be improved.
Embodiment 2
Below, based on brief description of the drawings embodiments of the invention 2. In Figure 10, dual suction type fromHeart pump is equipped with the impeller 53 being driven by main shaft 52 in the inside of shell 51. Shell 51 hasIn the axis of rotation direction of impeller 53, be positioned at the volute suction passage of the side of impeller 5354, and, the discharge stream 55 forming around the axis of rotation of impeller 53 there is.
Impeller 53 has stream 58 in impeller between wheel hub 56 and guard shield 57, at wheel hub 56Form multiple blades 59 with the assigned position of guard shield 57. In impeller, stream 58 utilizes towards impeller53 the suction oral area 60 of axis of rotation direction opening and the suction passage 54 of shell 51 are communicated with,And, utilize towards with the discharge oral area of the orthogonal radial direction opening of the axis of rotation of impeller 5361 are communicated with the discharge stream 55 of shell 51. Blade 59 joins wheel hub 56 and guard shield 57 toUpper, extend to the terminal location of discharging oral area 61 places from sucking the initiating terminal position of oral area 60.
Shell 51, in the internal face of suction passage 54 with impeller in the suction oral area of stream 5860 edge of opening is connected position around, has the axis of rotation direction protuberance to impeller 53Convex shaped part 62, convex shaped part 62 forms the terminal part towards the impeller 53 of suction passage 54.Convex shaped part 62 can pass through integrally formed in the time of cast casing 51 and arrange expeditiously.
Convex shaped part 62 forms the shape meeting the following conditions. That is, as shown in figure 10, when make fromBlade initiating terminal position in impeller in stream is till the impeller 53 on the summit of convex shaped part 62Distance in axis of rotation direction is B, in the axis of rotation direction of impeller 53, in impeller, flowsBlade initiating terminal position in road to suction oral area 60 subtends of impeller 53 volute outsideWhen distance till highest distance position on the internal face of the suction passage 54 of shell 51 is A, convexPortion 62 forms that to meet B/A be 0.23 to 0.31 condition. Preferably, form and meet B/A and beThe shape of 0.25 to 0.29 condition, more preferably, it is 0.27 to 0.28 that formation meets B/AThe shape of condition.
In said structure, revolve around axis of rotation by the driving of main shaft 52 at impeller 53Under the state turning, flow into the water of the suction passage 54 of shell 51, on one side along suction passage 54Spiral type rotation, on one side from the terminal part of suction passage 54 by the suction oral area of impeller 5354 flow into stream 58 in impeller. The water flowing into stream 58 in impeller, is subject to by impeller 53Rotation produce centrifugal force, from discharge oral area 61 spray to the discharge stream 55 of shell 51.
The current of rotation in the suction passage 54 of shell 51, in the terminal from suction passage 54When portion flows into the suction oral area 60 of impeller 53, in the direction of the axis of rotation along impeller 53On turn to. At this moment, the terminal part by suction passage 54 is to the axis of rotation direction of impeller 53Swell and form the convex shaped part 62 in above-mentioned number range, as shown by the arrows in Figure 10, canThe current that sharply turn to are slowed down, suppress the generation in hole, to improve the intake performance of pump, canGeneration, burn into inhibition by reduction, vibration and the noise of the pump performance causing in holeDamage.
Figure 11 be represent to become specific rate Ns280, in the pump that is equipped with shell and impeller, flowIn 54%, 75%, 100%, 118% the situation that amount is best efficiency point discharge rate QSuction specific rate S3% when B/A reduces by 3% with the lift of the value as expression pump suction performanceThe curve map of relation.
Figure 12 be represent to become specific rate Ns280, being equipped with in the pump of shell and impellerThe curve map of the relation of the highest efficiency eta max of B/A and pump.
In addition, in Figure 11, B/A=0.17 is the pump in the prior art shown in Figure 13In experimental data, the S3 value during with the best efficiency point (η max, 100%Q) of this pump is doneFor benchmark, using the value of B/A with make S3 value in the situation of changes in flow rate as S3/S3 η maxDraw. Can find out, the in the situation that of any flow, be 0.23 to 0.31 at B/AScope in, all demonstrate excellent S3 value compared with the pump of prior art. And then, at B/AValue be in 0.25 to 0.29 scope, more preferably, in 0.27 to 0.28 scope, aobviousMore excellent S3 value is shown.
Why make B/A have so appropriate scope, its reason is, little at B/AIn situation, because water (flow) direction changes to impeller with angle sharply, intake performance reduces, whenWhen B/A becomes large, due to suction passage reduced width, suck the flowing path section area reducing of volute chamber,The flow velocity flowing into impeller rises, and thus, intake performance reduces.
On the other hand, as can be seen from Figure 12, be accompanied by the increase of B/A, Efficiency Decreasing,But in above-mentioned number range, the reduction of efficiency is suppressed to bottom line, can improveIntake performance. In addition, in the pump of Ns140, Ns400, also confirm to be suitable for same scope.
In addition, as can be seen from Figure 11, in the region of the flow lower than 100%Q (54%Q,75%Q, 86%Q), this effect is large especially.
The present invention also can be by being combined the structure of the structure of embodiment 1 and embodiment 2Realized, by be equipped with the structure of embodiment 1 described above in a centrifugal pump simultaneouslyAnd the structure of embodiment 2, can further suppress the generation in hole, performance intake performance enters oneThe excellent effect that step improves.
In embodiment 1 and 2, represent integrally formed convex shaped part in the time of the casting of shell 5162 situation. But convex shaped part 62 can form and independently annular component of shell 51, andUtilize bolt etc. to be installed on shell 51. In this case, by changing annular component, canSo that the highest efficiency eta max of intake performance S3 and pump is adjusted to appropriate value.
In addition, in embodiment 1 and 2, represent and dual suction type centrifugal pump has been described, still,The present invention also can be applied to that suction inlet and rotary body meet at right angles or tool configures angularly and towardsThe pump of the form that the current of impeller sharply turn to, for example, multistage single inhalation type centrifugal pump.
Claims (11)
1. a centrifugal pump, is characterized in that, has impeller around the impeller of axis of rotation rotationInterior stream and the blade being configured in the interior stream of impeller, in impeller, stream has the rotation to impellerThe suction oral area of axis direction opening and to the discharge oral area of the radial direction opening of impeller,
Shell around impeller has: the side that is positioned at impeller in the axis of rotation direction of impellerAnd the volute suction passage being communicated with the suction oral area of impeller and around the rotating shaft of impellerThe discharge stream that is formed centrally and is communicated with the discharge oral area of impeller,
In the internal face of suction passage with impeller in around the edge of opening of suction oral area of streamConnected position forms to the convex shaped part of the axis of rotation direction protuberance of impeller,
This convex shaped part, will be accompanied by the speed composition, of radial direction of impeller by currentThe summit that radial direction flow velocity passes through and with the orthogonal straight line of the axis of rotation of impeller as the first baseLine, separates predetermined distance by the axis of rotation direction from the first baseline along impeller to impeller sideThe orthogonal plane of the position of h and the axis of rotation of impeller, as datum level, will be passed through datum levelWith the intersection of the inner peripheral surface of convex shaped part and the line parallel with the axis of rotation of impeller as the second baselineSituation under, from aforementioned summit to the first baseline with the distance L x of the intersection point of the second baseline,Around the axis of rotation of impeller, the radial direction flow velocity of current becomes maximum radial direction streamThe afore-mentioned distance Lxa at speed maximum position place, than becoming minimum radius side at radial direction flow velocityAfore-mentioned distance Lxb to flow velocity minimum position place is large, this convex shaped part from the first baseline to alongDistance H till the edge of opening of the suction oral area of the axis of rotation direction of impeller, at impellerThe surrounding of axis of rotation is constant.
2. centrifugal pump as claimed in claim 1, is characterized in that,
This convex shaped part forms the shape meeting the following conditions, and described condition is: to flow in impellerBlade initiating terminal position in road till the distance of the axis of rotation direction on the summit of convex shaped part beB, with in the axis of rotation direction of impeller from the blade initiating terminal position in stream in impeller toWith in the internal face of the suction passage of the volute shell of the suction oral area subtend of impeller farthestDistance till position is A, and B/A is 0.23 to 0.31.
3. centrifugal pump as claimed in claim 1, is characterized in that, convex shaped part comprising halfFootpath direction flow velocity maximum position is in interior aforementioned distance in the predetermined distance scope of circumferential directionFrom Lxa, larger than the afore-mentioned distance Lxb at radial direction flow velocity minimum position place.
4. centrifugal pump as claimed in claim 1, is characterized in that, the inner peripheral surface shape of convex shaped partThe curved surface of the convex that becomes to change smoothly towards the axis of rotation side of impeller.
5. centrifugal pump as claimed in claim 1, is characterized in that, the inner peripheral surface shape of convex shaped partThe curved surface that becomes to change smoothly along circumferential direction.
6. centrifugal pump as claimed in claim 1, is characterized in that, the inner peripheral surface shape of convex shaped partThe curved surface of the convex that becomes to change smoothly with circular arc towards the axis of rotation side of impeller, from radiusDirection flow velocity maximum position till in circumferential direction the position of 120 °, afore-mentioned distance Lx ratioThe afore-mentioned distance Lxb at radial direction flow velocity minimum position place is large.
7. centrifugal pump as claimed in claim 2, is characterized in that, it is 0.25 that formation meets B/AThe shape of the condition to 0.29.
8. centrifugal pump as claimed in claim 1 or 2, is characterized in that, convex shaped part is independentThe removable convex shaped part forming in shell.
9. centrifugal pump as claimed in claim 1 or 2, is characterized in that, convex shaped part and shellIntegrally formed.
10. centrifugal pump as claimed in claim 1 or 2, is characterized in that, convex shaped part is by encirclingShape member forms, and is arranged on shell.
11. centrifugal pumps as claimed in claim 1 or 2, is characterized in that, described centrifugal pump beThe dual suction type centrifugal pump of the chlamydate suction passage of both sides tool of the axis of rotation direction of impeller.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009268176A JP2011111956A (en) | 2009-11-26 | 2009-11-26 | Centrifugal pump |
| JP2009-268176 | 2009-11-26 | ||
| PCT/JP2010/057399 WO2011065039A1 (en) | 2009-11-26 | 2010-04-27 | Centrifugal pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102667176A CN102667176A (en) | 2012-09-12 |
| CN102667176B true CN102667176B (en) | 2016-05-04 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080053381.XA Active CN102667176B (en) | 2009-11-26 | 2010-04-27 | Centrifugal pump |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2011111956A (en) |
| CN (1) | CN102667176B (en) |
| WO (1) | WO2011065039A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2484305C1 (en) * | 2011-12-09 | 2013-06-10 | Общество с ограниченной ответственностью "Нефтекамский машиностроительный завод" (ООО "НКМЗ") | Main oil electric pump unit, and method for improvement of unit characteristics |
| KR101567534B1 (en) | 2014-10-21 | 2015-11-10 | 주식회사 조은펌프 | Pump Having Suction Casing with Flow Guides |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2556405Y (en) * | 2002-07-01 | 2003-06-18 | 长沙通大集团汩罗制泵有限公司 | Single-stage double-entry centrifugal dirty water pump |
| CN201246345Y (en) * | 2008-09-12 | 2009-05-27 | 常州东申泵业有限公司 | Double-suction split pump |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6149195A (en) * | 1984-08-17 | 1986-03-11 | Kubota Ltd | Double suction type spiral pump |
| JPH03290096A (en) * | 1990-04-05 | 1991-12-19 | Kubota Corp | Prerotation type centrifugal pump |
| CN101408196B (en) * | 2003-06-18 | 2011-06-01 | 三菱电机株式会社 | Blower |
-
2009
- 2009-11-26 JP JP2009268176A patent/JP2011111956A/en active Pending
-
2010
- 2010-04-27 WO PCT/JP2010/057399 patent/WO2011065039A1/en active Application Filing
- 2010-04-27 CN CN201080053381.XA patent/CN102667176B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2556405Y (en) * | 2002-07-01 | 2003-06-18 | 长沙通大集团汩罗制泵有限公司 | Single-stage double-entry centrifugal dirty water pump |
| CN201246345Y (en) * | 2008-09-12 | 2009-05-27 | 常州东申泵业有限公司 | Double-suction split pump |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2011111956A (en) | 2011-06-09 |
| CN102667176A (en) | 2012-09-12 |
| WO2011065039A1 (en) | 2011-06-03 |
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