CN1190597C - Turbine machine - Google Patents
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- CN1190597C CN1190597C CN 00104647 CN00104647A CN1190597C CN 1190597 C CN1190597 C CN 1190597C CN 00104647 CN00104647 CN 00104647 CN 00104647 A CN00104647 A CN 00104647A CN 1190597 C CN1190597 C CN 1190597C
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Abstract
In order to improve the rising characteristics on the right side of a flow rate characteristic curve of a pressure head of a turbine and inhibit the increase of the vibration and/or the noise of the turbine, a plurality of first grooves 24 are formed on the internal flowing surface of a machine shell along the circumference in the machine shell in the pressure gradient direction of fluid and used for connecting the inlet side of impeller blades and the internal flowing surface region of the machine shell of the impeller blades, and furthermore, second grooves 25 are formed in the internal flowing surface region of the machine shell of the impeller blades along the circumferential direction and used for communicating the first grooves along the circumferential direction of the machine shell.
Description
Technical field
The present invention relates to turbo type pumping device, especially related to a kind of turbo type pumping device that can prevent flow instability, because it can be suppressed at the vortex that the impeller eye place refluxes and causes, and can suppress the stall of impeller, and irrelevant with the type and the fluid of turbo type pumping device.
In more detail, the present invention relates to have the turbo type pumping device of non-volume type impeller, as pump, compressor, blower etc., especially, related to a kind of turbo type pumping device that can prevent flow instability, it can suppress by the vortex of the main flow of impeller eye place backflow or component generation or pre-vortex, and can suppress the stall of impeller, be applicable to mixed flow pump, mixed flow pump can be widely used as the water-circulating pump in thermoelectricity plant or the nuclear power plant, perhaps is used as drainage pump etc.
Background technique
According to used fluid of machine works and its pattern, the rotary machine that is called " turbo type pumping device " can be classified as follows:
1. according to the used fluid of machine:
Liquids and gases.
2. according to pattern
Axial flow, mixed-flow and centrifugal.
Since easy to operate, mixed flow pump mainly or extensively adopted now, and it comprises an inlet box, a pump and a Diffuser according to being from upstream to the downstream order.
(impeller) blade that rotates in the pump casing drives in rotating shaft with being rotated, thereby provides energy to the liquid that sucks from inlet box.Diffuser has the function that a part of speed energy (or kinetic energy) of liquid is transformed into static pressure.
Comprise that the typical characteristics curve is shown in the accompanying drawing 2 of back between the pressure head of turbo type pumping device of mixed flow pump and the flow rate, wherein horizontal axis is represented the flow rate parameter, and vertical shaft is represented the pressure head parameter.That is to say, descend at low flow rate district pressure head usually, become opposite relation, but when flow rate was positioned at certain given zone, the pressure head on the curve right side has with flow rate increased the characteristic that raises with the flow rate increase.But, when further being increased to, flow rate surpasses rising district, characteristic right side, and then pressure head descends along with the increase of flow rate again.
For adopt this right side to raise turbo type pumping device situation that characteristic flow rate carries out work, liquid quality is vibrated by self, that is to say, produces a kind of surging phenomenon.Can think, the characteristic that this right side raises is because backflow causes, though when the flow rate of the turbo type pumping device of flowing through is hanged down, occur refluxing in the impeller eye outside, but because the flow passage or the channel narrows of liquid inflow this moment impeller, thereby because the influence of above-mentioned backflow produces vortex in the liquid that flows into impeller.
Because surge not only jeopardizes turbo type pumping device, and jeopardize pipeline or the pipeline that is connected with turbo type pumping device upstream or downstream side, forbid usually at low flow rate district use turbo type pumping device.In addition, except the improvement of blade shape (being profile), advised suppressing surge, to reach the purpose of expansion or expansion turbo type pumping device working zone in order to following method.
1. casing is handled:
In the casing district at impeller place, form the thin or narrow groove or the draining hole of 10% to 20% blade chord length, thereby improve the stall margin.That is to say, adopt the casing advised to handle, the enough dark groove of formation in the casing inner wall (being flow surface) of blade location, they are along axial, circumferential or oblique, perhaps respectively along radially or oblique.
2. isolator:
In low flow rate district, provide an isolator to come that the backflow that takes place is gone up in the impeller eye outside and be divided into flow the backward part and the part (promptly along main flow direction) that flows forward, thereby forbidden the expansion that refluxes.
As the example of the isolator that is used for axial-flow turbine formula pumping installations, advised the suction ring type, blade is isolated and the air insulated formula.
In sucking ring type, reverse flow is closed in outside the inhaled loop, in blade is isolated, provides a fin between casing and ring.In addition, in the air insulated formula, the front end of movable wing (being blade) or most advanced and sophisticated being opened wide, thus reverse flow is introduced outside the casing, rely on fin to forbid the vortex that produces by reverse flow thus.Therefore, compare with above-mentioned preceding two kinds of patterns, it is more effective, but its equipment size is big.
3. ACTIVE CONTROL:
It sprays into high-pressure liquid or inject the backflow scene from the outside, suppresses the vortex that produces because of refluxing.
In addition, as the example of conventional turbo type pumping device, below mixed flow pump will be described.For mixed flow pump, need express a pressure head-flow characteristic curve (hereinafter referred to as " pressure head curve "), it under operative scenario on the whole flow range, in order to work quietly, should not have the phenomenon of right side rising at pump.But, in pump, in general, for example represent the efficient of pump performance, stability, the hole performance of pressure head curve and the various characteristicses such as axial motive force that are used to dam usually, homogeneous phase is mutually inverse relationship.That is to say that if want to improve one of them characteristic, then another or several characteristic will descend, so problem is to be difficult to reach to improve two or more at least characteristics simultaneously.For example, for the pump of main its efficient of consideration, the pressure head curve is expressed significant rising phenomenon at its right side branch, thereby has unsettled tendency.
For the pressure head curve that obtains descending continuously on the right side, as above mentioned so that can stably work, the known casing that provides is handled or isolator in routine techniques.For example at U.S. Patent number 4,212, this structure has been described in 585.
In addition, also advised a kind of turbo type pumping device, wherein, on the casing flow surface, form many grooves, so that between the casing flow surface position at impeller eye side and blade place or zone, connect, obtain not having the pressure head curve of this right side rising characteristic thus, suppressed backflow simultaneously at the blade inlet place.
But, casing according to above-mentioned prior art is handled and isolator, though can move on to characteristic curve between pressure head that comprises the right side raised portion and the flow rate one side of low flow rate, thereby expanded its stable working zone, but it can not remove or eliminate characteristic or phenomenon that the right side raises.In addition, handle according to casing, if the every increase by 10% in stall margin, then turbo type pumping device reduces about 1% efficient.
In addition, in this ACTIVE CONTROL, because need as its whole system, reduce the efficient of turbo type pumping device from turbo type pumping device proper or its outside high-pressure liquid that obtains.
In addition, for this turbo type pumping device, wherein, the groove that forms is used for connecting between the casing flow surface at impeller eye side and blade place, groove easy to manufacture, and turbo type pumping unit efficiency reduces less, also can obtain not having in its characteristic this right side elevated pressure cephalic flexure line.But it is not considered when vanes is crossed the many grooves that form on the casing flow surface, owing to fluid and the interference between the groove from impeller blade may produce pressure pulsation, thereby has increased vibration and noise.
Summary of the invention
According to the present invention, a purpose provides a kind of turbo type pumping device, and it has pressure head-flow characteristic that right side rising phenomenon is improved, and can suppress the reduction of its efficient, can also suppress the increase of its vibration and noise.
According to the present invention, another purpose provides a kind of turbo type pumping device, and it has improved pressure head-flow characteristic with respect to the turbo type pumping device with enclosed impeller, and the reduction that can suppress its efficient with and the increase of vibration and noise.
The first, according to the present invention, in order to achieve the above object, provide a kind of turbo type pumping device, it comprises: a casing; An impeller, it has many blades and is positioned at said machine casing; A plurality of first grooves, they are formed on the internal surface of said machine casing, are used for being communicated with between the inner surface section of the said machine casing at the blade place of the inlet side of above-mentioned impeller and above-mentioned impeller; It is characterized by, on the internal surface of said machine casing, form at least one the second grooves, be used for circumferentially connecting above-mentioned a plurality of first grooves along said machine casing.
According to the present invention, be preferably in the turbo type pumping device of above regulation, the width of above-mentioned many first grooves is equal to or greater than 5mm, make the overall width of above-mentioned many first grooves be above-mentioned impeller blade place the said machine casing internal surface inner circumferential length about 30% to 50%, and the degree of depth is equal to or greater than 2mm, make it be above-mentioned impeller blade place the said machine casing inner surface diameter about 0.5% to 1.6%.
In addition, according to the present invention, be preferably in the turbo type pumping device of afore mentioned rules, above-mentioned second groove is formed on the said machine casing internal surface at above-mentioned impeller blade place.Also be preferably in the turbo type pumping device of afore mentioned rules, the degree of depth that above-mentioned second groove forms is equal to or shallower than above-mentioned first groove.
In addition, according to the present invention, be preferably in the turbo type pumping device of afore mentioned rules, above-mentioned second groove is formed on the internal surface of said machine casing, it is from the above-mentioned first groove clearing end in above-mentioned turbo type pumping device downstream side, zone up to above-mentioned impeller blade place is perhaps up to the inlet side of above-mentioned impeller.
The second, according to the present invention, provide a kind of turbo type pumping device, it comprises: a casing; An impeller, it has many blades and is positioned at said machine casing; And many grooves, they are along the pressure gradient direction of fluid, be formed on the internal surface of said machine casing, be used between the said machine casing inner surface section at above-mentioned impeller eye side and above-mentioned impeller blade place, being communicated with, wherein longshore current body pressure gradient direction forms above-mentioned groove, makes them from tilting towards downstream one side of above-mentioned turbo type pumping device and the sense of rotation of above-mentioned impeller near the impeller eye district.
The 3rd, according to the present invention, provide a kind of turbo type pumping device, it comprises: a casing; An impeller, it has many blades and is positioned at said machine casing; Many first grooves, they are along the pressure gradient direction of fluid, and are formed on along the casing inner circumference on the said machine casing internal surface of above-mentioned impeller eye side; , second groove, it is formed on the internal surface of said machine casing, and the zone at above-mentioned impeller blade place is along the circumferencial direction of casing; And a flow channel, be used between above-mentioned first groove and above-mentioned second groove, connecting.
In addition, according to the present invention, in the turbo type pumping device of above regulation, above-mentioned flow channel groove, hole, formations such as pipeline or pipeline, and the internal surface of bypass said machine casing.
The 4th, according to the present invention, provide a kind of turbo type pumping device, it comprises: a casing; An impeller, it has many blades and is positioned at said machine casing; Many first grooves, they are along the pressure gradient direction of fluid, and are formed on along the casing inner circumference on the casing inner surface of above-mentioned impeller eye side; , second groove, it is formed on the internal surface of said machine casing, and the zone at above-mentioned impeller blade place is along the circumferencial direction of casing; Article one, three-flute, it is formed on the said machine casing internal surface, near above-mentioned impeller blade front, along the circumferencial direction of casing; And flow channel, be used between above-mentioned first groove and above-mentioned second groove, connecting, wherein above-mentioned flow channel is formed on the line that stretches out from above-mentioned first groove, and the internal surface of bypass said machine casing makes and leads to by above-mentioned three-flute and above-mentioned first concentrated flow.
The 5th, according to the present invention, provide a kind of turbo type pumping device, it comprises: a casing; An impeller, it has many blades and is positioned at said machine casing; Many grooves, they are along the pressure gradient direction of fluid, and are formed on the said machine casing internal surface along the casing inner circumference, are used for being communicated with between the said machine casing inner surface section at above-mentioned impeller eye side and above-mentioned impeller blade place; And many movable parts, they are arranged in the above-mentioned groove of longshore current body pressure gradient direction, can be along the moving radially of said machine casing, thus change the degree of depth of above-mentioned groove.
The 6th, according to the present invention, provide a kind of turbo type pumping device, it comprises: an enclosed impeller, it has many blades and around the outer cover of blade; A casing, it has interior mobile wall and has held above-mentioned impeller, and wherein above-mentioned impeller forms open type, does not have the outer cover around it near above-mentioned impeller eye; And many first grooves, they are along the pressure gradient direction, and be formed on along the casing inner circumference on the interior mobile wall of said machine casing, near impeller eye facing to above-mentioned do not have outer cover around above-mentioned impeller part, wherein, be positioned at the upstream of the most advanced and sophisticated inlet side of above-mentioned impeller at the starting end of above-mentioned first groove of inlet side, and the clearing end of above-mentioned first groove is positioned at the downstream of above-mentioned impeller tips inlet side; Turbo type pumping device also comprises: one second groove, it is used for circumferentially connecting above-mentioned many first grooves along said machine casing, it is formed on the interior mobile wall of said machine casing, near impeller eye facing to above-mentioned do not have outer cover around above-mentioned impeller part.
The 7th, according to the present invention, provide a kind of turbo type pumping device, it comprises: an impeller, a casing, it has held above-mentioned impeller; Many first grooves, they are along the pressure gradient direction of fluid, be formed on the internal surface of said machine casing, the outer periphery part that on the impeller eye side, faces toward above-mentioned impeller blade, be used for connecting between the said machine casing inner surface section at above-mentioned impeller eye side can reflux when flow rate is low zone and the most advanced and sophisticated place of above-mentioned impeller blade, wherein, in turbo type pumping device downstream side, the final position of above-mentioned first groove makes and can take out pressure fluid, be used for inlet, suppress to produce in the main flow and reflux at above-mentioned first groove of turbo type pumping upstream side; And one second groove, it is being formed on the internal surface of said machine casing near the above-mentioned impeller eye, is used for circumferentially connecting above-mentioned many first grooves along casing, wherein, the said machine casing that above-mentioned first and second grooves are set has partly formed an entity, separates with the other parts of said machine casing.
According to the present invention, adopted the structure of second groove, it is formed on the zone of the above-mentioned groove at impeller blade place, its degree of depth is shallower than, and equals or is deeper than first groove, and a part that makes first groove is along circumferentially continuously, reduce or relaxed pressure pulsation, this pressure pulsation be at impeller blade through along the groove of pressure gradient direction the time, because groove and cause from the interference between the impeller fluid can suppress thus by impeller pulsation-induced vibration and/or generating noise.
In addition, form groove (i.e. first groove), and it is tilted with above-mentioned wheel rotation direction (promptly with opposite coiling of crooked impeller blade direction), also can reduce or relax from the interference between impeller fluid and the groove along the impeller gradient direction.
In addition, formation along first groove of pressure gradient direction upward to impeller eye, but make them not with overlapping along the second circumferential groove, make and to be interconnected along circumferential groove with along the groove of pressure gradient direction, can obtain same effect, take out pressure fluid thus and be used to be suppressed at the interior backflow of impeller eye place main flow.Above-mentioned this two classes groove preferably connects by flow channel, and passage is formed on the casing outer periphery, and breaks away from the casing inner surface of main current flow warp.At this moment, in the casing inner surface zone at impeller blade place, can not provide this groove, can reduce or relax thus from the interference between impeller fluid and the groove along the pressure gradient direction.Be used for preferably being formed on the line that prolongs from first groove, make the inlet side that flows into impeller blade with the reverse fluid of main flow at the flow channel that first groove and second groove connect.
Description of drawings
According to the following explanation of doing with reference to accompanying drawing, will be clearly according to other characteristic, purpose and/or advantage that the present invention drew.
Fig. 1 is according to the first embodiment of the present invention, the meridian plane view of a mixed flow pump major component;
Fig. 2 is the figure that represents turbo type pumping device pressure head-flow characteristic curve and efficient-flow characteristic curve respectively;
Fig. 3 is the figure that concerns between expression turbo type pumping device flow rate and the vibration acceleration;
Fig. 4 is the figure that concerns between expression turbo type pumping device flow rate and the vibration noise magnitude;
Fig. 5 is the meridian plane view of turbo type pumping device major component, has represented a kind of variation pattern that the present invention is embodiment illustrated in fig. 1;
Fig. 6 is the expansion view of casing inner surface shown in Figure 1;
Fig. 7 is the expansion view of casing inner surface, has represented a kind of variation pattern of example shown in Figure 6;
Fig. 8 is the expansion view of casing inner surface, has represented the another kind of variation pattern of example shown in Figure 6;
Fig. 9 is the expansion view of casing inner surface, has represented second embodiment of the present invention;
Figure 10 (a) and (b) represented the 3rd embodiment of the present invention, especially, Figure 10 (a) has represented the expansion view of casing inner surface, Figure 10 (b) has represented the A-A sectional view (meridian plane view) of Figure 10 (a);
Figure 11 (a) has represented to reach the object lesson of third embodiment of the invention structure to (c), especially, Figure 11 (a) has represented the expansion view of casing inner surface, Figure 11 (b) has represented the A-A sectional view (meridian plane view) of Figure 11 (a), and Figure 11 (c) has represented the B-B sectional view (meridian plane view) of Figure 11 (a);
Figure 12 is the meridian plane view of turbo type pumping device major component, has represented Figure 10 (a) and (b) a kind of variation pattern of illustrated embodiment;
Figure 13 (a) and (b) represented the Figure 10 (a) and (b) the another kind of variation pattern of illustrated embodiment, especially, Figure 13 (a) has represented the expansion view of casing inner surface, Figure 13 (b) has represented the A-A sectional view (meridian plane view) of Figure 13 (a);
Figure 14 is the view of four embodiment of the invention, and especially, Figure 14 (a) has represented the state of movable part 34 along the skew of external diameter direction, and Figure 14 (b) has represented the state of movable part 34 along the internal diameter direction skew;
Figure 15 is the meridian plane view of embodiment's major component, and first embodiment of the invention wherein shown in Figure 1 is applied to a turbo type pumping device, and this turbo type pumping device has adopted the enclosed impeller with outer cover;
Figure 16 is the sectional view along XIII-XIII line among Figure 15; And
Figure 17 (a) to (d) has represented the various examples of the slot cross-section shape that forms on casing inner surface.
Embodiment
Describe each embodiment of the present invention in detail hereinafter with reference to accompanying drawing.
Fig. 1 has represented first embodiment of the present invention.This figure is as the part amplification view of the mixed-flow pump impeller part of turbo type pumping device representative, wherein numbers 1 and has represented an open type impeller with unlimited blade.In order to suppress backflow, near the intake section of impeller blade 22,, a large amount of shallow slots 24 (i.e. first groove) of longshore current body pressure gradient direction on casing 2 internal surfaces, have been formed around the inner circumference of casing 2 from the adverse current generation of impeller blade.This groove is arranged in the impeller blade region at the final position a in turbo type pumping device downstream side, thereby make a part of fluid that is compressed by impeller flow to position b by this groove 24, if when turbo type pumping upstream side flow rate is hanged down, can produce backflow at position b.Thus, because inject the position that is easy to produce backflow at the fluid in downstream side, the generation that can suppress to reflux, and suppress because the influence that refluxes makes the main flow at turbo type pumping device portal place become vortex, thereby obtained having high performance turbo type pumping device, forbidden the generation of impeller blade stall.
In addition,, on the internal surface of casing, also formed many second grooves 25 according to present embodiment, make with the corresponding part in impeller blade region on, many first grooves 24 that form on the casing inner circumference are continuous.For the situation that does not form this second groove, can affirm, disturb mutually from the fluid of impeller 1 first groove 24 that (being the pressure gradient direction of longshore current body) forms with vertically, thereby produce pressure pulsation.Pressure pulsation makes the vibration of turbo type pumping device, has increased vibration and noise.According to the present invention, because in the impeller blade location, formed along the second circumferential groove 25 of casing, relaxed in second groove 25 along the pressure reduction between many first grooves 24 of casing inner circumference formation, can make the pressure pulsation that causes by first groove 24 and blade 22 diminish thus, promptly suppress because the vibration that pressure pulsation causes and the increase of noise.
Fig. 2 has represented a plotted curve, and it has represented turbo type pumping device pressure head-flow characteristic curve and efficient-flow characteristic curve, and wherein horizontal axis is represented its nondimensional flow rate, and vertical shaft is represented its nondimensional pressure head.In the figure, white circle is represented the pressure head-flow characteristic curve and the efficient-flow characteristic curve of turbo type pumping device, does not wherein form first groove 24 around casing on internal surface.Black circle is represented the pressure head-flow characteristic curve and the efficient-flow characteristic curve of turbo type pumping device, has wherein formed first groove 24.White triangle is represented the pressure head-flow characteristic curve and the efficient-flow characteristic curve of turbo type pumping device, has wherein formed first groove 24, has also formed second groove 25 near groove 24 final positions in turbo type pumping device downstream side.
As ise apparent from FIG. 2, in white circle situation, in from 0.5 to 0.6 the dimensionless flow rate zone, have the characteristic that raises on the right side, wherein the boost pressure head along with flow rate also increases.In black circle situation, the characteristic that the right side raises disappears.In white triangle situation, prove to have the effect identical with black circle according to present embodiment.
Fig. 3 has represented the relation between the flow rate and vibration acceleration in the turbo type pumping device, and wherein white circle, black circle and white triangle have been represented the data on the turbo type pumping device same as shown in Figure 2 respectively.In the figure, horizontal axis is represented its dimensionless flow rate, and vertical shaft is represented its dimensionless vibration acceleration.As ise apparent from FIG. 3, compare with white circle situation, in having formed the black circle situation of first groove, vibration acceleration demonstrates a peak value near 0.5 to 0.6 dimensionless flow rate, and compare with white circle situation, the vibration on the gamut is increased.In contrast, in the white triangle situation that first and second grooves all form, compare with black circle situation, obviously improved vibration acceleration greatly, and near 0.5 to 0.6 dimensionless flow rate, vibration acceleration does not have this peak value, thereby has improved vibration greatly yet.
Fig. 4 has represented the relation between the flow rate and noise magnitude in the turbo type pumping device, and wherein white circle, black circle and white triangle have been represented the data on the turbo type pumping device same as shown in Figure 2 respectively.In the figure, horizontal axis is represented its dimensionless flow rate, and vertical shaft is represented its dimensionless noise magnitude.As ise apparent from FIG. 4, compare with white circle situation, the noise magnitude is increased in black circle situation.Opposite with the situation that only forms first groove, in white triangle (according to the present embodiment) situation that first and second grooves all form, in the high efficiency flow rate range of expression as pump groundwork scope, the noise magnitude is greatly diminished, and drops to and the roughly the same degree of the situation that does not form this groove in casing (white circle situation).
But, in the embodiment shown in fig. 1, the depth as shallow along the depth ratio of circumferential second groove 25 along pressure gradient direction first groove 24, and be communicated with a large amount of all first grooves or several first grooves that form on the casing inner circumference.
In addition, these degree of depth along circumferential second groove 25 can equal along the degree of depth of first groove 24 of pressure gradient direction, can also do greater than the degree of depth of first groove.
In addition, for the position that forms along circumferential second groove 25, though in example shown in Figure 1, they are near the front c of impeller blade 22, from the position of the upstream of groove final position a one side, point to downstream one side of turbo type pumping device, still up to slightly, they can point to downstream one side (referring to dotted line 25a) of turbo type pumping device from extending to the final position a of groove near the front c of impeller blade 22.In addition, as shown in Figure 5, can be arranged to second groove 25 to extend to slightly from the impeller blade region of its upstream one side from groove final position a, perhaps they can be from groove final position a, extends to the position of turbo type pumping device upstream one side of upstream more than blade 22 front c.
Fig. 6 has represented the expansion view of casing inner surface shown in Figure 1, can find out in the figure, has been communicated with a large amount of all first grooves 24 along the pressure gradient direction that form on the casing inner circumference along circumferential second groove 25 of casing along circumferential.As shown in Figure 7, can be circumferential along second groove 25 that casing is circumferential along casing, form intermittently with its number, made their several grooves a large amount of first grooves that on the casing inner circumference, form that have been communicated with (or connection) along the pressure gradient direction.In addition, as shown in Figure 8, can form spiral way, up to the final position of first groove 24, make circumferentially to be interconnected along casing along first groove 24 of pressure gradient direction near beginning impeller blade first inlet region along the second circumferential groove 25.
Below, with reference to Fig. 9 second embodiment of the present invention is described.
In the present embodiment, following characteristic is also identical with above-mentioned first embodiment: form many grooves 24 along pressure gradient direction (promptly axial), be used for being communicated with between the inlet side of impeller blade and casing inner surface zone.In this embodiment, with above-mentioned impeller blade region (being downstream one side of blade) corresponding groove 24 parts and wheel rotation direction inclination (or coiling).Adopt this structure, make interference between impeller blade 22 and the groove 24 become slowly or loosen, thereby can reduce the generation of pressure pulsation, and suppressed the increase of vibration and noise.In addition, in the axial formation of the groove 24 of impeller blade upstream side along casing, when pressure is increased, fluid flow back into the inlet side of impeller blade by these grooves 24, penetrate on the position that makes it when flow rate is low, can reflux, thereby can suppress because the circulation of the impeller blade cause of refluxing/or stall, relax thus or reduced the characteristic that the right side raises in turbo type pumping device pressure head-flow characteristic curve.
Figure 10 (a) and (b) represented the view of third embodiment of the invention.Figure 10 (a) has represented the expansion view of casing inner surface, and Figure 10 (b) has represented the A-A sectional view on Figure 10 (a) meridian plane.
On the internal surface of casing 2, many first grooves 24 have been formed within it on the circumference, be used to connect impeller eye side and impeller region along axial (being the pressure gradient direction), and on the casing inner surface at impeller place, form second groove 25, and itself is along circumferentially continuous.In addition, the internal surface of lie casing and formed flow channel 27 makes above-mentioned first groove 24 and second groove 25 be interconnected.Flow channel 27 is positioned at or the length direction of alignment slot 24, and therefore flow through second groove 25 and flow channel 27 of a part of fluid that is compressed by impeller blade enters first groove 24, makes to penetrate on the position of the meeting generation circulation of the inlet side of impeller blade.Thus, situation same as the previously described embodiments can relax the characteristic that the right side raises in turbo type pumping device pressure head-flow characteristic curve.
In addition, locating along the axial impeller place of casing, on casing inner surface, do not form this groove, therefore this interference when crossing first groove, vanes does not take place in fluid, in addition by second groove 25, make the pressure reduction between many first grooves 24 diminish, can suppress the vibration that causes by pressure pulsation and the increase of noise thus.
The example of realizing above-mentioned the 3rd example structure is described with reference to Figure 11 (a) to (c).Figure 11 (a) has represented the expansion view of casing inner surface, and Figure 11 (b) has represented A-A sectional view (being the sectional view on the meridian plane) among Figure 11 (a), and Figure 11 (c) has represented B-B sectional view (being the sectional view on the meridian plane) among Figure 11 (a).
Vertically casing is divided into three parts, represents with numbering 28,29 and 30.(here, if 28 and 29 parts of casing form one or integral body, if perhaps 29 of casing and 30 parts form one or integral body all it doesn't matter.) on the internal surface 28 of casing, formed on the circumference within it along axial many first grooves 24 of (being the pressure gradient direction), be connected to blade front c from the inlet side of impeller blade.In addition, on the inner periphery side 29 of housing part, insert a circle or ring part 31 (being casing), thus between this circular piece end face and casing end face 30 in turbo type pumping device downstream side, along circumferentially having formed second groove 25.In addition,, formed flow channel 27, made first and second grooves 24 and 25 be interconnected at the dorsal surface of above-mentioned circular piece 31.Shown in Figure 11 (c), casing inner surface 29 is connected on the outer surface that does not form slot part on the circular piece 31, can be fixed to circular piece 31 on the internal surface 29 of casing spare.
Below, above-mentioned a kind of variation pattern embodiment illustrated in fig. 10 will be described in Figure 12.With Figure 10 (a) and (b) different characteristics be: adopt pipeline or pipeline to constitute and walk around the flow channel that casing inner surface is provided with.To this, by second groove 25 and flow channel 32, got back in first groove 24 facing to main current flow by the fluid that impeller blade compresses, on the position that meeting takes place to reflux, penetrate thus.
At Figure 13 (a) with the another kind of variation pattern of embodiment shown in above-mentioned Figure 10 will be described (b).Figure 13 (a) has represented the expansion view of casing inner surface, and Figure 13 (b) has represented the A-A sectional view among Figure 13 (a).
This variation pattern and Figure 10 (a) and (b) different characteristics be: on blade 22 front c, formed on the casing inner surface, be used for circumferentially being communicated with second groove 25 and separate and a large amount of vertically first groove 24 that forms along casing along the circumferential three-flute 33 of casing.By flow channel 27 second groove 25 and three-flute 33 are interconnected, have constituted thus and make the fluid that is compressed by impeller blade 22 flow through second groove 25, flow channel 27 and three-flute 33 and enter first groove 24.
By second groove 25 and the three-flute 33, when pressure pulsation that impeller blade 22 is caused by interference during through first groove 24 has reduced pressure reduction between each first groove that forms in a large number on the casing inner circumference, can be suppressed at the vibration that causes owing to pressure pulsation in the turbo type pumping device and the increase of noise thus.
With reference to Figure 14 (a) and (b) explanation the 4th embodiment of the present invention.
In this embodiment, many shallow slots 24 on the internal surface of casing 2, have been formed along the pressure gradient direction, be used between the casing inner surface district at inlet side and impeller place, being communicated with, in every groove 24, be provided with a movable part 34, it has the thickness littler than groove depth, can move along radially (promptly along Vertical direction).Movable part 34 makes and can be positioned on the curvilinear surface identical with casing 2 internal surfaces.
Adopt this structure of present embodiment, the working area of right side rising characteristic takes place in turbo type pumping device pressure head-flow characteristic curve, movable part 34 is along external diameter direction biasing or mobile, shown in Figure 14 (a), on casing inner surface, form shallow slot 24 thus, flow through groove 24 and flowing back in the main flow of a part of fluid that is compressed by impeller blade 22, and be launched into the zone that to reflux in the impeller blade ingress, thereby suppressed generation at impeller eye side ring stream, and the stall of impeller blade, can relax or reduce the characteristic that the right side raises in turbo type pumping device pressure head-flow characteristic curve thus.
In addition, the working area of right side rising characteristic takes place in pressure head-flow characteristic curve, and shown in Figure 14 (b), movable part 34 is along internal diameter direction biasing or mobile, make the movable part internal surface consistent, caused the state that on casing, does not have this shallow slot thus with casing inner surface.Like this,, can make casing inner surface be in the state that does not form groove, disturb, relax pressure pulsation thus thereby can loosen the fluid that causes because of blade and axial groove because in the working area that above-mentioned right side rising characteristic does not take place.
In this case, can obtain such effect according to present embodiment: on whole flow rate range, can relax because vibration and the noise that the axial groove influence produces.
Figure 15 has illustrated an example, wherein, uses first embodiment of the invention in a turbo type pumping device (for example, an enclosed mixed flow pump), and it has adopted enclosed impeller, and impeller has an outer cover as its part.Figure 16 has represented along the sectional view of XIII-XIII among Figure 15.
In enclosed impeller 1, be provided with an outer cover 1a.But this outer cover 1a is not located near the 1c of impeller blade inlet, and impeller is made the form that calls semi-open impeller, and outer cover is not set on its part.In the inner diameter district of most of outer cover, be provided with a mouse shape ring district 1b, facing on its motionless side, on the internal surface of casing 2, be provided with a casing ring 5.Between mouse shape ring district 1b and casing ring 5, constituted the seal area of rotation axis.Shown in Figure 15 and 16, near 1c impeller blade inlet, facing to do not have this outer cover around impeller blade, on the inner circumference of casing 2 internal surfaces, arranged many first grooves 24 vertically with equidistant around the casing circumference.The final position of groove in turbo type pumping device downstream side is positioned near the position (promptly the inlet at impeller blade that enters the downstream side from the impeller blade front slightly, contiguous or near the position of mouse shape ring district 1b), and be positioned at than an impeller blade front side of upstream more at the final position b of turbo type pumping upstream side.The position that constitutes facing to the regional 2g of the casing 2 of impeller outer cover end face 1d with vertically much at one at groove 24 final positions in downstream side, and with the surface of casing axis normal on.This surface (promptly should zone) 2g and outer cover end face 1d face toward mutually with axial distance δ 1.Near the zone of first groove 24 vertically at impeller blade place, numbering 25 has been represented second groove that forms along circumferentially, and this groove 25 is communicated with first groove that forms on the casing inner circumference, and more shallow than first groove.
If turbo type pumping device (being pump) is in low flow rate regional work, with the backflow (being reverse flow) that takes place as shown in figure 15.According to the present invention, adopt above-mentioned this structure, a part of fluid that is compressed by impeller flow back into the final position b of upstream side from the final position a in downstream side in first groove.Because form groove 24 along pump shaft line direction, the fluid that flows in groove is along the component of wheel rotation direction, and is launched in the position that can reflux when flow rate is low, thereby weakens or discerned backflow, thus, and the generation that can suppress to reflux.Therefore, can prevent or be suppressed at the impeller eye side because vortex or the pre-vortex that refluxes and cause, and the stall of impeller blade, thereby the reduction of theoretical pressure head is diminished, improved the rising characteristic on pressure head in the turbo type pumping device-flow characteristic curve right side thus.
In addition, owing to there is second groove 25, can reduce or relax and when blade 22 process axial grooves 24, cause the impeller pulsation that interference causes, also can reduce and relax the pressure reduction between the groove 24 thus, thereby can suppress such phenomenon:, increased vibration and noise thus because the impeller pulsation makes the vibration of turbo type pumping device.
Though in the foregoing description closed mixed flow pump is described, the present invention also can be applicable to other turbo type pumping device, and as centrifugal pump, mixed flow blower, mixed flow compressor etc., each can have open impeller or enclosed impeller.
In addition, (being the FPG direction) vertically groove 24 sectional shapes or the form that forms on casing inner surface except rectangle, also can be made triangularity, circle or trapezoidal, arrives shown in (d) as Figure 17 (a ).Groove 25 and 33 also can make same sectional shape.
The pump work flow rate of pumping plant is being determined on a point that intersects between static pressure head, resistance curve and the pumping pressure head-rating curve, the static pressure head is determined that by head or water-head between suction side in the pumping plant and the discharge side resistance curve is determined by the resistance sum in passage in the pumping plant or the path.If have the district that raises, then may intersect at many somes upward pressure head-rating curves and resistance curve on pressure head-rating curve right side.At this moment, can not only go up on one point and determine intersection point, that is to say, can not determine flow rate uniquely, therefore can not determine flow rate.Especially, when the very high and pipe resistance of static pressure head is very little, become clearly.
In routine techniques, maximal efficiency and pressure head stability are made balance, thereby draw the pressure head-rating curve of the phenomenon that do not raise on the right side, therefore may make maximal efficiency that the tendency of reduction is arranged slightly.In addition, have the situation of range of instability in pump, the working area of pump must be in the zone that does not have this unstable operation generation, and the working zone is narrowed down.Therefore,,, must take such measure: increase the quantity of pump, make the flow of each pump diminish, thereby the operation point of each pump is moved on on the point outside the unstable region in the situation that work enters unstable region for a pumping plant.Adopt above-mentioned the present invention, can relax the problem of this routine techniques.In addition, according to the present invention, adopt along the structure of slotting on the casing periphery, can reduce because of axial groove with from disturbing the pressure pulsation that causes to produce between the impeller fluid, reduced pump main body and ducted vibration and noise thus, they are caused by the vibration with pressure pulsation pump.Therefore, adopt the present invention, can obtain such effect: turbo type pumping device has high performance and the characteristic that do not have this right side to raise, resulting turbo type pumping device even also can be used for contiguous uptown pumping plant etc.
The present invention can reach very big effect when being used for mixed flow pump, especially ought be used for having the pump of a special speed Ns as indication pump characteristics index, can reach significant effect, and special speed is expressed as follows:
Ns=N * Q
0.5/ H
0.75≈ 1,000 to 1,500
Here establishing rotating speed is N (rpm), a total pressure H (rice), and discharge flow rate Q (per minute cubic meter).
Especially when being used for following pump, can reach very big effect: wherein, be equal to or greater than 50% of regulation point upward pressure head by sucking water level and discharging the definite static pressure head of water level.
Taked following structure according to the present invention: many first grooves are used for being communicated with between the casing inner surface district at impeller eye side and impeller place, and many second grooves are used to be communicated with along circumferential many first grooves of casing, can obtain such turbo type pumping device thus: it has improved pressure head-flow characteristic, especially the rising characteristic on right side, can suppress the reduction of turbo type pumping unit efficiency, with and the increase of vibration and noise.
In addition, take the structure of many longshore current body pressure gradient direction grooves, and be provided with radially moveable spare, make the degree of depth of groove to change, also can reach above-mentioned same or analogous effect.
In addition, according to the present invention, near the semi open type structure that impeller eye, does not form outer cover, in be applied to the to have enclosed impeller turbo type pumping device of (impeller has outer cover), the turbo type pumping device that also can obtain having above-mentioned same or similar effect.
Claims (15)
1. turbo type pumping device, it comprises:
A casing (2);
An impeller (1), it has many blades (22) and is positioned at said machine casing (2);
A plurality of first grooves (24), they are formed on the internal surface of said machine casing (2), are used for being communicated with between the inner surface section of the said machine casing (2) at blade (22) place of the inlet side of above-mentioned impeller (1) and above-mentioned impeller (1); It is characterized by,
On the internal surface of said machine casing (2), form at least one the second grooves (25), be used for circumferentially connecting above-mentioned a plurality of first grooves (24) along said machine casing (2).
2. turbo type pumping device as claimed in claim 1, it is characterized by, the width of above-mentioned a plurality of first grooves (24) is equal to or greater than 5mm, make the overall width of above-mentioned a plurality of first grooves (24) be above-mentioned impeller (1) blade (22) place said machine casing (2) internal surface inner circumferential length about 30% to 50%, the degree of depth of above-mentioned a plurality of first grooves (24) is equal to or greater than 2mm, make it be above-mentioned impeller blade (22) place said machine casing (2) inner surface diameter about 0.5% to 1.6%.
3. turbo type pumping device as claimed in claim 1 is characterized by, and above-mentioned second groove (25) is formed on the internal surface of said machine casing (2) at blade (22) place of above-mentioned impeller (1).
4. turbo type pumping device as claimed in claim 1 is characterized by, and the degree of depth of above-mentioned second groove (25) is equal to or less than the width of above-mentioned first groove (24).
5. turbo type pumping device as claimed in claim 1 is characterized by, and the degree of depth of above-mentioned second groove (25) is deeper than above-mentioned first groove (24).
6. turbo type pumping device as claimed in claim 1 is characterized by, and above-mentioned a plurality of second grooves (24) circumferentially form intermittently along said machine casing (2).
7. turbo type pumping device as claimed in claim 1, it is characterized by, above-mentioned second groove (25) on the internal surface of said machine casing (2) from the position, front of the blade (22) of above-mentioned impeller (1) or near the position extend to the zone at blade (22) place of above-mentioned impeller (1), perhaps extend to the clearing end of first groove (24).
8. turbo type pumping device as claimed in claim 1, it is characterized by, above-mentioned second groove (25) extends to the zone at blade (22) place of above-mentioned impeller (1) from above-mentioned first groove (24) clearing end of above-mentioned turbo type pumping device downstream one side on the internal surface of said machine casing (2), perhaps extend to the inlet side of above-mentioned impeller (1).
9. turbo type pumping device as claimed in claim 1, it is characterized by, above-mentioned second groove (25) forms on the internal surface of said machine casing (2) in a spiral manner, and it extends to the above-mentioned first groove clearing end of above-mentioned turbo type pumping device downstream one side from the inlet side of above-mentioned impeller (1) always.
10. turbo type pumping device as claimed in claim 1 is characterized by, and the part (28,29) that is provided with on the said machine casing (2) of above-mentioned first and second grooves (24,25) has formed an entity, separates with another part (30) of said machine casing (2).
11. turbo type pumping device as claimed in claim 1 is characterized by, and makes the downstream side of above-mentioned first groove near the position the entrance part of impeller (1) to above-mentioned turbo type pumping device, to the sense of rotation inclination of above-mentioned impeller (1).
12. turbo type pumping device as claimed in claim 1 is characterized by, and a flow channel (27,32) is set, and is used for connecting between above-mentioned first groove (24) and above-mentioned second groove (25).
13. turbo type pumping device as claimed in claim 12 is characterized by, above-mentioned flow channel (27,32) comprises groove, hole, pipeline and ducted one and the internal surface of bypass said machine casing (2) at least.
14. turbo type pumping device as claimed in claim 1 is characterized by, and also comprises:
Article one, three-flute (33), it is formed on said machine casing (2) internal surface, near blade (22) front of above-mentioned impeller (1), along the circumferencial direction of casing; And
, a flow channel (27), be used to connect above-mentioned second groove (25) and above-mentioned three-flute (33), the length direction conllinear of above-mentioned flow channel (27) and above-mentioned first groove (24), and the internal surface of bypass said machine casing (2), make it pass through above-mentioned three-flute (33) and be communicated with above-mentioned first groove (24).
15. turbo type pumping device as claimed in claim 1 is characterized by, except that near the open section inlet, impeller (1) comprises outer cover (1a) around above-mentioned blade (22), and second groove (25) that faces toward of open section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 00104647 CN1190597C (en) | 2000-03-20 | 2000-03-20 | Turbine machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 00104647 CN1190597C (en) | 2000-03-20 | 2000-03-20 | Turbine machine |
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| Publication Number | Publication Date |
|---|---|
| CN1314552A CN1314552A (en) | 2001-09-26 |
| CN1190597C true CN1190597C (en) | 2005-02-23 |
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| CN 00104647 Expired - Fee Related CN1190597C (en) | 2000-03-20 | 2000-03-20 | Turbine machine |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101946094A (en) * | 2008-02-21 | 2011-01-12 | Mtu飞机发动机有限公司 | Circulation structure for a turbo compressor |
| US10823194B2 (en) | 2014-12-01 | 2020-11-03 | General Electric Company | Compressor end-wall treatment with multiple flow axes |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20090118922A (en) * | 2007-02-14 | 2009-11-18 | 보르그워너 인코퍼레이티드 | Compressor housing |
| FR2929349B1 (en) * | 2008-03-28 | 2010-04-16 | Snecma | CARTER FOR MOBILE WHEEL TURBOMACHINE WHEEL |
| FR2970302B1 (en) * | 2011-01-11 | 2015-07-17 | Snecma | DOUBLE FLOW TURBOREACTOR |
| JP6866019B2 (en) * | 2014-06-24 | 2021-04-28 | コンセプツ エヌアールイーシー，エルエルシー | Flow control structure of turbomachinery and its design method |
| CN105268040B (en) * | 2014-07-22 | 2018-04-17 | 王辉山 | A kind of centrifugal blood pump of magnetic coupling driving |
| CN105673553A (en) * | 2016-03-18 | 2016-06-15 | 江苏大学 | Diagonal flow pump |
| JP6770594B2 (en) * | 2017-02-08 | 2020-10-14 | 三菱重工エンジン＆ターボチャージャ株式会社 | Centrifugal compressor and turbocharger |
-
2000
- 2000-03-20 CN CN 00104647 patent/CN1190597C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101946094A (en) * | 2008-02-21 | 2011-01-12 | Mtu飞机发动机有限公司 | Circulation structure for a turbo compressor |
| US10823194B2 (en) | 2014-12-01 | 2020-11-03 | General Electric Company | Compressor end-wall treatment with multiple flow axes |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1314552A (en) | 2001-09-26 |
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