CN100406746C - Centrifugal compressor and manufacturing method for impeller - Google Patents
Centrifugal compressor and manufacturing method for impeller Download PDFInfo
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- CN100406746C CN100406746C CNB2005800002491A CN200580000249A CN100406746C CN 100406746 C CN100406746 C CN 100406746C CN B2005800002491 A CNB2005800002491 A CN B2005800002491A CN 200580000249 A CN200580000249 A CN 200580000249A CN 100406746 C CN100406746 C CN 100406746C
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Abstract
A centrifugal compressor and a method of manufacturing an impeller, the method wherein a projected part (17) is formed at the approximately radial center part of the impeller (11) on the negative pressure surface side of its a blade (16) so as to form a curve from the leading edge part (A) to the throat part (B) thereof. The projected part (17) is formed to be curved and then to be flat from the throat part (B) to the trailing edge part thereof. The projected part (17) is formed at a position where the relative inflow velocity of the fluid into the impeller (11) is nearly 1 in Mach number Ma. Thus, since an operating efficiency can be increased and an applicable flow range can be increased, the performance of the impeller can be increased.
Description
Technical field
The present invention relates to a kind of centrifugal compressor that liquid pressure rise is formed compressed fluid, particularly be used for manufacture method the impeller and the impeller of liquid pressure rise.
Background technique
Figure 20 is the sectional drawing of the impeller of centrifugal compressor in the past, Figure 21 is the XXI-XXI sectional drawing of Figure 20, Figure 22 is the skeleton diagram of shape of each position of representing the blade of impeller in the past, and Figure 23 is expression corresponding to the chart of the flow of the per unit area of the relative inflow velocity of the fluid of in the past centrifugal compressor.
General centrifugal compressor is supported with the impeller with a plurality of blades with rotating freely in case, form along axial suction path with respect to this impeller, and formed along scatterer (diffuser) radially.So when utilizing not shown motor rotary blade, then fluid will pass the suction path and be inhaled in the case, boosted back is by the scatterer ejection in flowing through the process of impeller, and here the kinetic pressure of compressed fluid is converted into static pressure.
In this kind centrifugal compressor, as Figure 20 and shown in Figure 21, impeller 001 is made of a plurality of blades 004 that are fixed in wheel hub 003 on the running shaft 002, become to be fixed in radially the peripheral part of this wheel hub 003.As a rule, when the blade 004 of this impeller 001 is set, adopt following method, promptly, outer circumferential side shape (sleeve lateral lobe plate shape), interior all side shapes (hub side blade shape) of decision blade 004 are by linking the global shape that decides blade with both with straight line.
When described centrifugal compressor was used as the centrifugal compressor of high-pressure ratio, the flow rate of fluid of intake impeller 001 will surpass velocity of sound, for example, as shown in figure 20, at hub side (H) Mach number
, at central part (M) Mach number
, at sleeve side (S) Mach number
Thus, will be formed in hub side becomes subsonic speed, becomes ultrasonic transonic speed impeller in the sleeve side, particularly produces shock wave from central part towards the sleeve side.Like this, under the very big situation of this shock wave, the flowing of blade surface will be peeled off and make impeller stall, thereby produces efficient or performance reduces such problem.
So the method as solving this kind problem for example has following patent documentation 1.In the technology described in this patent documentation 1, by the following processing of meridian plane shape with impeller blade, promptly, with the bight of the outer circumferential side of the end of leading edge according to the size of the speed composition that makes the vertical inflow blade in the middle of the air-flow that is sucked with respect to leading edge less than producing the mode of impacting wave propagation velocity, make the shape of cutting off obliquely, and the relative inflow velocity of air-flow is suppressed to prevent the generation of shock wave for less than the boundary speed that produces shock wave.
Patent documentation 1: the spy opens flat 08-049696 communique
But, when the impeller 001 of described centrifugal compressor is in the past used as the centrifugal compressor of high-pressure ratio, the slit width of adjacent vanes 004 will be set its central part (M) according to the mode that changes point-blank between sleeve side (S) hub side (H), the bending of blade 004 is risen in order all to obtain identical pressure in sleeve side and hub side, is designed according to compare the bigger mode of steering angle that makes hub side with the sleeve side.Consequently, as shown in figure 22, on impeller 400, with respect to the blade imagination flow path width W of front edge A
S, W
M, W
H, the slit width W at slit portion B place
Sth, W
Mth, W
HthBecome big, in addition, become big until the ratio of the variation of the flow path area of slit portion B in hub side, diminish in the sleeve side from front edge A.
Thus, even as described shown in the patent documentation 1, the shape that the bight of outer circumferential side of the meridian plane shape of impeller blade being made the end of leading edge has cut off with being tilted also can't reduce the shock wave that the variation that is accompanied by flow path area produces.
That is, when flow path area is increased, be in above Mach number
The intermediate portion M of blade and the sleeve side S place Mach number in supersonic speed zone increase, be in less than Mach number
The hub side H place Mach number of blade in subsonic speed zone reduce.Like this, because flow path area is relevant with the flow of per unit area, so the relation of Mach number and flow just becomes the parabolical relation as shown in the chart of Figure 23.
So as shown in figure 23, when fluid was inhaled into, because flow path area increases when flowing to slit portion B (△) from front edge A (●), therefore the flow Q of the per unit area of this moment located to reduce variation delta Q in hub side (H)
H, Mach number Ma locates from Ma in hub side (H)
HABe reduced to Ma
HBOn the other hand, locate to reduce variation delta Q at central part (M)
M, (S) locates to reduce variation delta Q in the sleeve side
S, (M) locates from Ma at central part
MAIncrease to Ma
MB, (S) locates from Ma in the sleeve side
SAIncrease to Ma
SBAt this moment, because the variation delta Q of the flow of per unit area
MGreater than variation delta Q
STherefore, be appreciated that the increasing amount Δ Ma of the Mach number of intermediate portion
MIncreasing amount Δ Ma greater than the Mach number of sleeve side
S
Like this, in the centrifugal compressor of high-pressure ratio, when fluid when front edge A flows into slit portion B reduce owing to be accompanied by the flow of the increase per unit area of flow path area, therefore particularly at the central part radially of blade, Mach number will increase widely.Thus, will produce very big shock wave here, make the efficient of impeller or performance reduce, the efficient of compressor self reduces, and the range of flow that can stably move reduces.
Summary of the invention
The present invention is the scheme that solves this kind problem, and its purpose is, provides by improving running efficiency to enlarge the range of flow that can adapt to and can realize the centrifugal compressor of raising of performance and the manufacture method of impeller.
Be used to realize that the centrifugal compressor of the present invention of described purpose is to have set the impeller that becomes to have installed radially a plurality of blades at the peripheral part of wheel hub rotatably in the inside of case, the centrifugal compressor that utilizes the rotation of described impeller will import the liquid pressure rise in the described case and spray, it is characterized in that the slit portion of the suction surface side of described blade is relatively made convex along the fin height direction.
Centrifugal compressor of the present invention is characterised in that the slit portion of the suction surface side of described blade has been made into convex on the section of fin height direction.
Centrifugal compressor of the present invention is characterised in that, in the suction surface side of described blade, the relative inflow velocity that flows to the fluid of described impeller has been made into convex near reaching the fin height position of mach one.
Centrifugal compressor of the present invention is characterised in that, at the slit portion of the suction surface side of described blade, the roughly intermediate portion radially of this blade has been made into convex.
Centrifugal compressor of the present invention is characterised in that, at the slit portion of the suction surface side of described blade, the roughly intermediate portion radially of this blade has been made convex according to the mode that forms curve.
Centrifugal compressor of the present invention is characterised in that, at the slit portion of the suction surface side of described blade, the roughly intermediate portion radially of this blade has been made convex according to the mode that forms the peak shape.
Centrifugal compressor of the present invention is characterised in that the suction surface side quilt of described blade is according to making towards the mode that described slit portion gradually becomes convex from front edge.
Centrifugal compressor of the present invention is characterised in that the suction surface side quilt of described blade is according to making towards the dirty mode that gradually becomes plane from the described slit portion that has been made into convex.
Centrifugal compressor of the present invention is characterised in that the suction surface side quilt of described blade is according to making towards the dirty smooth gradually mode that becomes concavity then from the described slit portion that has been made into convex.
Centrifugal compressor of the present invention is characterised in that, at the slit portion of the suction surface side of described blade, described hub side has been made into concavity.
The feature of the manufacture method of impeller of the present invention is, can set the impeller that becomes to have installed radially a plurality of blades at the peripheral part of wheel hub rotatably for inside at case, and the rotation that utilizes described impeller will import the liquid pressure rise in the described case and the centrifugal compressor that sprays, the described vane trailing edge inclination of the axial rotary that makes cutting tool oblique under the state of given angle, begin the suction surface side of this blade of cutting from the front edge side of described blade, slit portion is relatively made convex.
According to centrifugal compressor of the present invention, owing to can dispose the impeller that becomes to have installed radially a plurality of blades rotatably in the inside of case, the slit portion of the suction surface side of each blade has relatively been made convex along the fin height direction, therefore slit width diminishes, the variation of the flow path area on the flow direction of fluid reduces, changes in flow rate also reduces, so the increase of Mach number is suppressed, the size of the shock wave that is produced also is suppressed, peeling off or being out of shape of fluid reduces and prevents the reduction of the efficient or the performance of impeller, consequently, because of running efficiency improves, just can improve performance by enlarging the range of flow that can adapt to.
According to centrifugal compressor of the present invention, because the slit portion of the suction surface side of blade has been made convex on the section of fin height direction, therefore the central part of the fin height direction of blade just becomes convex, and can be suppressed at the size of the shock wave that produces on this position reliably.
According to centrifugal compressor of the present invention, because the suction surface side of blade is reached near the mode that becomes convex the fin height position of mach one makes according to the relative inflow velocity that makes the fluid that flows to impeller, therefore the central part radially of blade just is made into convex, thereby can be suppressed at the size of the shock wave that produces on this position reliably.
According to centrifugal compressor of the present invention, because the slit portion of the suction surface side of blade is made according to the mode that the roughly intermediate portion radially that makes blade becomes convex, therefore make convex by the position that will be easy to generate shock wave, just can reduce the size of shock wave reliably.
According to centrifugal compressor of the present invention, because the slit portion of the suction surface side of blade is made convex according to the mode that the roughly intermediate portion radially that makes blade forms curve, therefore be made as the convex that has formed curve by the suction surface side with blade, that just can not hinder fluid fluidly dwindles slit width.
According to centrifugal compressor of the present invention, because the slit portion of the suction surface side of blade is made convex according to the mode that the roughly intermediate portion radially that makes blade forms the peak shape, therefore be made as the convex that has formed the peak shape by suction surface side with blade, that just can not hinder fluid fluidly dwindles slit width, and it is more easy that the cutting of face becomes, and can improve processability.
According to centrifugal compressor of the present invention since with the suction surface side of blade according to making towards slit portion from front edge with gradually becoming convex, so just can not hinder fluid fluidly dwindle slit width.
According to centrifugal compressor of the present invention since with the suction surface side of blade according to making towards the mode that hinder marginal part gradually becomes plane from slit portion, that therefore just can not hinder fluid fluidly dwindles slit width.
According to centrifugal compressor of the present invention since with the suction surface side of blade according to making towards the smooth gradually mode that becomes concavity then of hinder marginal part from the slit portion that has been made into convex, therefore just can not hinder the compressed fluid effectively fluidly of fluid.
According to centrifugal compressor of the present invention,, therefore just can make the mobile smooth and easy of fluid and the raising performance because the slit portion of the suction surface side of blade is made according to the mode that makes hub side become concavity.
Manufacture method according to impeller of the present invention, owing to be the centrifugal compressor that can set to become to have installed radially the impeller of a plurality of blades in case inside rotatably, the axial rotary vane trailing edge inclination that makes cutting tool oblique under the state of given angle, begin the suction surface side of cutting blade from the front edge side of blade, slit portion is relatively made convex, therefore just the processing of blade face can be easily carried out at short notice, thereby processability can be improved.
Description of drawings
Fig. 1 be embodiments of the invention 1 centrifugal compressor want portion's sectional drawing.
Fig. 2 is the II-II sectional drawing of Fig. 1.
Fig. 3 is the III-III sectional drawing of Fig. 1.
Fig. 4 is the skeleton diagram of impeller of embodiment 1 centrifugal compressor.
Fig. 5 is the skeleton diagram of manufacture method of impeller of expression embodiment's 1 centrifugal compressor.
Fig. 6 is the skeleton diagram of the processing sequence of expression impeller.
Fig. 7 is the skeleton diagram of shape of central part of blade of expression embodiment's 1 impeller.
Fig. 8 is the chart of expression corresponding to the flow of the per unit area of the relative inflow velocity of the fluid of embodiment 1 centrifugal compressor.
Fig. 9 be embodiments of the invention 2 centrifugal compressor want portion's sectional drawing.
Figure 10 is the X-X sectional drawing of Fig. 9.
Figure 11 is the skeleton diagram of impeller of embodiment 2 centrifugal compressor.
Figure 12 is the skeleton diagram of manufacture method of impeller of expression embodiment's 2 centrifugal compressor.
Figure 13 is the sectional drawing of impeller of the centrifugal compressor of embodiments of the invention 3.
Figure 14 is the skeleton diagram of the centrifugal compressor of embodiments of the invention 4.
Figure 15 is the sectional drawing of the positive upper reaches of slit portion of embodiment 4 impeller.
Figure 16 is the sectional drawing of the positive upper reaches of slit portion of embodiment 4 impeller.
Figure 17 is the sectional drawing of the positive upper reaches of slit portion of embodiment 4 impeller.
Figure 18 is the plan view of embodiment 4 blade.
Figure 19 is the skeleton diagram that the section shape of expression embodiment's 4 blade changes.
Figure 20 is the sectional drawing of the impeller of centrifugal compressor in the past.
Figure 21 is the XXI-XXI sectional drawing of Figure 20.
Figure 22 is the skeleton diagram of each locational shape of representing the blade of impeller in the past.
Figure 23 is the chart of expression corresponding to the flow of the per unit area of the relative inflow velocity of the fluid of in the past centrifugal compressor.
Wherein, 11,31,41, the 51-impeller, 12, the 32-running shaft, 15, the 33-wheel hub, 16, the 34-blade, 17, the 35-protuberance, 21-cutting tool, 42-recess, 52-par.
Embodiment
Embodiment to the manufacture method of centrifugal compressor of the present invention and impeller is elaborated below with reference to accompanying drawings.And the present invention is not limited by this embodiment.
Fig. 1 be embodiments of the invention 1 centrifugal compressor want portion's sectional drawing, Fig. 2 is the II-II sectional drawing of Fig. 1, Fig. 3 is the III-III sectional drawing of Fig. 1, Fig. 4 is the skeleton diagram of impeller of embodiment 1 centrifugal compressor, Fig. 5 is the skeleton diagram of manufacture method of impeller of expression embodiment's 1 centrifugal compressor, Fig. 6 is the skeleton diagram of the processing sequence of expression impeller, Fig. 7 is the skeleton diagram of shape of central part of blade of expression embodiment's 1 impeller, and Fig. 8 is the chart of expression corresponding to the flow of the per unit area of the relative inflow velocity of the fluid of embodiment 1 centrifugal compressor.
The centrifugal compressor of present embodiment utilizes running shaft 12 to support impeller 11 in not shown case as shown in Figures 1 to 4 with rotating freely, forms along axial suction path 13 with respect to this impeller 11, and forms along scatterer 14 radially.So when utilizing not shown motor rotary blade 11, fluid promptly passes suction path 13 and is inhaled in the case, boosted back is by scatterer 14 ejections in the process that flows through impeller 11, and here the kinetic pressure of compressed fluid is converted into static pressure.
In this kind centrifugal compressor, impeller 11 is at the peripheral part that is fixed in the wheel hub 15 on the running shaft 12, become to be fixed with radially a plurality of blades 16, the global shape of this blade 16 determines the central part shape by outer circumferential side shape (sleeve lateral lobe plate shape), interior all side shapes (hub side blade shape) decision by both are linked with straight line.
In addition, the centrifugal compressor of present embodiment is the centrifugal compressor corresponding to high-pressure ratio, and the flow rate of fluid that is inhaled into impeller 11 surpasses velocity of sound.That is, on the blade 16 of impeller 11, infer at hub side (H) Mach number
, at central part (M) Mach number
, at sleeve side (S) Mach number
Thus, will be formed in hub side becomes subsonic speed, becomes ultrasonic transonic speed impeller 11 in the sleeve side.Like this, in this kind transonic speed impeller 11, in general, owing to utilize the rotation of blade 16, with respect to the imaginary flow path width of front edge A, the width of blade of slit portion B (slit width) increases and the flow path area increase, therefore flow reduces, Mach number increases, and particularly produces shock wave from central part towards the sleeve side, thus problem efficient or that performance reduces.
So, in the present embodiment, in the centrifugal compressor that is so constituted, in each blade 16, the slit portion of suction surface side is made according to the mode that relatively becomes convex on the section of fin height direction (fin is radially).Promptly, the suction surface of blade 16 (sense of rotation back) quilt is according to making protuberance 17 from front edge A until the mode that slit portion B formation curve gradually becomes convex (arcuation), and these protuberance 17 quilts are according to making towards the mode that hinder marginal part gradually becomes plane from slit portion B.Like this, this protuberance 17 just is formed on the roughly intermediate portion radially of blade 16, and the relative inflow velocity that promptly flows to the fluid of impeller 11 reaches Mach number
Near.
At this moment, blade 16 is at front edge A place, shown in detailed among Fig. 2, formation is along radially rectilinear form, and pressure side side and suction surface side all become tabular surface, and at slit portion B place, shown in detailed among Fig. 3, formation is to the curve shape of sense of rotation the place ahead bending, and the pressure side side becomes recess shapes, and the suction surface side becomes the protuberance shape.
In addition, the blade 16 that has a protuberance 17 at the slit portion B of suction surface side is to utilize the method that the following describes to make.As Fig. 5 and shown in Figure 6, the cutting tool 21 that uses cephalic par to be made very thinly, its running shaft O to the trailing edge inclination of blade 16 oblique under the state of given angle, begin the suction surface side of cutting blade 16 from the front edge A of blade 16, slit portion B is made convex (protuberance 17), process to the trailing edge side.That is, under with the state of cutting tool 21,, make its running shaft O move to O by as shown in Figure 6 with the given speed rotation
1, O
2... O
10The time, in addition as shown in Figure 5, when making it continuously to swing along the face thickness direction, the cutting surface, B makes convex with slit portion.
Like this, in the impeller 11 of present embodiment, by on the slit portion B of the suction surface side of blade 16, forming protuberance 17, then as shown in figure 17, the slit width W of the central part of slit portion B
MthWith respect to slit width W in the past
Mth' diminish, diminish until the variable quantity (increasing amount) of the flow path area of slit portion B from front edge A.
So as shown in Figure 8, when fluid was inhaled into, because flow path area increases when flowing to slit portion B (△) from front edge A (●), therefore the flow Q of this moment located to reduce variation delta Q in hub side (H)
H, (M) locates to reduce variation delta Q at central part
M, (S) locates to reduce variation delta Q in the sleeve side
SAt this moment, Mach number Ma locates from Ma in hub side (H)
HABe reduced to Ma
HB, (M) locates from Ma at central part
MAIncrease to Ma
MB, (S) locates from Ma in the sleeve side
SAIncrease to Ma
SBAt this moment, owing to, on slit portion B, be formed with protuberance 17 at central part (M), therefore less until the variable quantity (increasing amount) of the flow path area of slit portion B from front edge A, the variable quantity of flow Q (reduction amount) Δ Q
MAlso less.Consequently, the increasing amount Δ Ma of the Mach number located of central part (M)
M(Figure 23) compared significantly and reduced with in the past.
Like this in embodiment 1 centrifugal compressor, suction surface side at the blade 16 of impeller 11, in substantial middle portion radially, form curve ground from front edge A until slit portion B and form protuberance 17, by this protuberance 17 is formed according to becoming plane mode from slit portion B towards hinder marginal part formation curve ground, will reach Mach number at the relative inflow velocity of the fluid that flows to impeller 11
The position form this protuberance 17.
So, because the slit width of the central part of impeller 11 diminishes, the variation of the flow path area on the flow direction of fluid reduces, changes in flow rate also reduces, therefore the increase of Mach number is suppressed, the size of the shock wave that is produced also is suppressed, fluid flow peel off or be out of shape minimizing, thereby prevented the efficient of impeller 11 or the reduction of performance.Consequently, because of running efficiency improves, just can improve performance by enlarging the range of flow that can adapt to.
In addition, by the cutting tool 21 that uses cephalic par to be formed very thinly, make its running shaft O under the state of the oblique given angle of trailing edge inclination of blade 16,, and slit portion B is being made convex (protuberance 17) from the suction surface of front edge A towards slit portion B ground cutting blade 16.So, just can easily and carry out the processing of the suction surface of blade 16 at short notice, thereby can improve processability.
Embodiment 2
Fig. 9 be embodiments of the invention 2 centrifugal compressor want portion's sectional drawing, Figure 10 is the X-X sectional drawing of Fig. 9, Figure 11 is the skeleton diagram of impeller of embodiment 2 centrifugal compressor, and Figure 12 is the skeleton diagram of manufacture method of impeller of expression embodiment's 2 centrifugal compressor.And, for have with foregoing embodiment in the member of the part identical functions that illustrates, use identical symbol, the explanation that repeats is omitted.
In embodiment 2 centrifugal compressor, to shown in Figure 11, impeller 31 becomes to be fixed with radially a plurality of blades 34 at the peripheral part that is fixed in the wheel hub 33 on the running shaft 32 as Fig. 9.On the suction surface of the blade 34 of this impeller 31, form curve (arcuation) and gradually become convex ground until slit portion B from front edge A and be formed with protuberance 35, this protuberance 35 is gradually become planely towards hinder marginal part from slit portion B to be formed.In addition, this protuberance 35 is formed on the roughly intermediate portion radially of blade 34, that is, reached according to the relative inflow velocity along the fluid that flows to impeller 31
The line mode that forms the peak shape form.
At this moment, blade 34 forms at front edge A place along rectilinear form radially, pressure side side and suction surface side all become tabular surface, yet at slit portion B place, shown in detailed among Figure 10, formation is to the shape of sense of rotation the place ahead bending, and the pressure side side becomes recess shapes, and the suction surface side becomes the protuberance shape.
In addition, the blade that has protuberance 35 on the slit portion B of suction surface side is stated bright method manufacturing below 34.As shown in figure 12, the cutting tool 21 that uses cephalic par to be made begins the suction surface side of cutting blade 34 from the front edge A of blade 34 very thinly, and slit portion B is made convex (protuberance 35), processes to the trailing edge side.At this moment, under with the state of cutting tool 21,, with 2 stage cutting surfaces, slit portion B is made the peak shape along the face thickness direction by when its running shaft O is moved with the given speed rotation.
Like this, in embodiment 2 centrifugal compressor, by according to suction surface side at the blade 34 of impeller 31, form curve from front edge A until slit portion B, and the mode that makes radially substantial middle portion become the peak shape forms protuberance 35, will reach at the relative inflow velocity of the fluid that flows to impeller 11
The position on form this protuberance 35.
So, the slit width of the central part of impeller 31 diminishes, the variation of the flow path area on the flow direction of fluid reduces, changes in flow rate also reduces, therefore the increase of Mach number is suppressed, the size of the shock wave that is produced also is suppressed, fluid flow peel off or be out of shape minimizing, thereby prevented the efficient of impeller 11 or the reduction of performance.
In addition, by the cutting tool 21 that uses cephalic par to be formed very thinly,, and slit portion B is made the protuberance 35 of peak shape from the suction surface of front edge A towards slit portion B ground cutting blade 34.
Figure 13 is the sectional drawing of impeller of the centrifugal compressor of embodiments of the invention 3.And, for have with foregoing embodiment in the member of the part identical functions that illustrates use identical symbol, the explanation that repeats is omitted.
In the centrifugal compressor of present embodiment, as shown in figure 13, the hub side during with any one of protuberance 35 of peak shape of impeller 31 of using described embodiment's 1 the protuberance 17 of impeller 11 or embodiment 2 is made concavity and is constituted impeller 41.Promptly, in the impeller 41 of present embodiment, gradually become formation protuberance 17 in convex ground from the suction surface of impeller 16 towards slit portion, perhaps on the suction surface of blade 34, gradually become convex ground from front edge until slit portion and form protuberance 35, this protuberance 17,35 is formed on the roughly intermediate portion radially of blade 16, that is, reached by the relative inflow velocity along the fluid that flows to impeller 11
Line form.In addition, on the suction surface of this blade 34, the mode according to the hub side slit width is enlarged is formed with the recess 42 that becomes concavity towards the pressure side side.
Like this, in embodiment 3 centrifugal compressor, according in the blade 16 of impeller 41 or 34 suction surface side, form curve from front edge A until slit portion B, and the mode that substantial middle portion radially becomes the peak shape forms protuberance 17 or 35, has formed the recess 42 that slit width enlarges in its hub side.So, because of the slit width of the central part of impeller 41 diminishes, on the other hand, enlarge at the hub side slit width, thereby make the variation of the flow path area on the flow direction of fluid reduce, changes in flow rate also reduces, therefore the increase of Mach number is suppressed, the size of the shock wave that is produced also is suppressed, and fluid mobile peeled off or be out of shape minimizing, thereby can improve the efficient and the performance of impeller 11 or 31.
Embodiment 4
Figure 14 is the skeleton diagram of the centrifugal compressor of embodiments of the invention 4, Figure 15, Figure 16, Figure 17 are the sectional drawings of the positive upper reaches of slit portion of embodiment 4 impeller, Figure 18 is the plan view of embodiment 4 blade, and Figure 19 is the skeleton diagram that the section shape of expression blade changes.
In the centrifugal compressor of present embodiment, as Figure 14 to shown in Figure 17, from by and the protuberance 17 of described embodiment's 1 impeller 11 slit portion 35 of having made convex in the same manner gradually become towards hinder marginal part and be formed flatly and constitute impeller 51.That is, in the impeller 51 of present embodiment, on the suction surface of blade 34, gradually become convex ground from front edge 35 until slit portion 35 and form protuberance 35, this protuberance 35 is formed on the roughly intermediate portion radially of blade 34, that is, reached by the relative inflow velocity along the fluid that flows to impeller 51
Line form ground, top and form.In addition, on the suction surface of this blade 34, form par 52 and become and identical in the past smooth shape until hinder marginal part from the protuberance 35 of slit portion.
At this moment, as Figure 17 and shown in Figure 180, the central part that the blade 34 of impeller 51 makes the suction surface side is given prominence to gradually with expanding and is formed protuberance 35 (a-d) until slit portion 54 from front edge 53, thereafter, this protuberance 35 is dug up and formed par 52 (d-f), become tabular surface once more.
Like this, in embodiment 4 centrifugal compressor, in the suction surface side of the blade 34 of impeller 51, form protuberance 35 until slit portion B in radially substantial middle portion from front edge A, form par 52 and change smooth shape into until hinder marginal part from the protuberance 35 of this slit portion.Consequently, it is big that the slit width of the central part of impeller 51 becomes, and compares to embodiment 3 with embodiment 1 to increase the slit area.So, in embodiment 4, utilize the effect of the protuberance of suction surface, the increase of Mach number is suppressed, and the size of the shock wave that is produced also is suppressed, the peeling off or be out of shape minimizing of fluid, thereby can improve the efficient and the performance of impeller 51, meanwhile, can prevent reduction by the flow of slit.In addition, the increase of Mach number is suppressed, and the size of the shock wave that is produced also is suppressed, fluid flow peel off or be out of shape minimizing, thereby can improve the efficient and the performance of impeller 51.
And, among described each embodiment, though the slit portion of the suction surface side of blade is made convex and the pressure side side has been made concavity, among the present invention, as long as the slit portion of the suction surface side of blade is relatively made convex.That is, be convex as long as make the slit portion of suction surface side with respect to pressure side side and front edge, the pressure side side is made tabular surface or convex can.
(industrial utilize possibility)
Centrifugal compressor of the present invention is that the slit portion of the suction surface side of the blade of impeller is made convex And reduce the centrifugal compressor of slit width, for the boats and ships supercharging of having used this centrifugal compressor Device, automobile use the small gas worm gear very useful with booster, industrial compressor, aviation.
Claims (11)
1. centrifugal compressor, be to have set the impeller that becomes to have installed radially a plurality of blades at the peripheral part of wheel hub rotatably in the inside of case, the centrifugal compressor that utilizes the rotation of described impeller will import to the liquid pressure rise in the described case and spray, it is characterized in that the slit portion of the suction surface side of described blade has relatively been made convex along the fin height direction.
2. centrifugal compressor according to claim 1 is characterized in that, the slit portion of the suction surface side of described blade has been made into convex in the section of fin height direction.
3. centrifugal compressor according to claim 1 and 2 is characterized in that, in the suction surface side of described blade, the relative inflow velocity that flows to the fluid of described impeller has been made into convex near reaching the fin height position of mach one.
4. centrifugal compressor according to claim 1 and 2 is characterized in that, at the slit portion of the suction surface side of described blade, the roughly intermediate portion radially of this blade has been made into convex.
5. centrifugal compressor according to claim 4 is characterized in that, at the slit portion of the suction surface side of described blade, the roughly intermediate portion radially of this blade has been made convex according to the mode that forms curve.
6. centrifugal compressor according to claim 4 is characterized in that, at the slit portion of the suction surface side of described blade, the roughly intermediate portion radially of this blade has been made convex according to the mode that forms the peak shape.
7. centrifugal compressor according to claim 1 and 2 is characterized in that, the suction surface side quilt of described blade is according to making towards the mode that described slit portion gradually becomes convex from front edge.
8. centrifugal compressor according to claim 7 is characterized in that, the suction surface side quilt of described blade is according to making towards the dirty mode that gradually becomes plane from the described slit portion that has been made into convex.
9. centrifugal compressor according to claim 7 is characterized in that, the suction surface side quilt of described blade is according to making towards the dirty smooth gradually mode that becomes concavity then from the described slit portion that has been made into convex.
10. centrifugal compressor according to claim 1 and 2 is characterized in that, at the slit portion of the suction surface side of described blade, described hub side has been made into concavity.
11. the manufacture method of an impeller, it is characterized in that, can set the impeller that becomes to have installed radially a plurality of blades at the peripheral part of wheel hub rotatably for inside at case, and the rotation that utilizes described impeller will import to the liquid pressure rise in the described case and the centrifugal compressor that sprays, the described vane trailing edge inclination of the axial rotary that makes cutting tool oblique under the state of given angle, from the suction surface side of this blade of front edge side cutting of described blade, slit portion is relatively made convex.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004084329 | 2004-03-23 | ||
| JP084329/2004 | 2004-03-23 | ||
| JP032121/2005 | 2005-02-08 |
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| CN1771397A CN1771397A (en) | 2006-05-10 |
| CN100406746C true CN100406746C (en) | 2008-07-30 |
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| CNB2005800002491A Expired - Fee Related CN100406746C (en) | 2004-03-23 | 2005-02-24 | Centrifugal compressor and manufacturing method for impeller |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102365464A (en) * | 2009-07-13 | 2012-02-29 | 三菱重工业株式会社 | Impeller and rotary machine |
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| US8668446B2 (en) * | 2010-08-31 | 2014-03-11 | General Electric Company | Supersonic compressor rotor and method of assembling same |
| US8864454B2 (en) * | 2010-10-28 | 2014-10-21 | General Electric Company | System and method of assembling a supersonic compressor system including a supersonic compressor rotor and a compressor assembly |
| US8827640B2 (en) * | 2011-03-01 | 2014-09-09 | General Electric Company | System and methods of assembling a supersonic compressor rotor including a radial flow channel |
| US8951009B2 (en) * | 2011-05-23 | 2015-02-10 | Ingersoll Rand Company | Sculpted impeller |
| CN103256248B (en) * | 2012-02-21 | 2015-08-26 | 珠海格力电器股份有限公司 | Impeller and comprise the centrifugal compressor of this impeller |
| DE102012212896A1 (en) * | 2012-07-24 | 2014-02-20 | Continental Automotive Gmbh | Impeller of an exhaust gas turbocharger |
| JP5522306B1 (en) * | 2012-12-21 | 2014-06-18 | ダイキン工業株式会社 | Centrifugal fan |
| DE112014003121T5 (en) * | 2013-07-04 | 2016-04-07 | Ihi Corporation | Compressor impeller, centrifugal compressor, compressor impeller machining method, and compressor impeller machining apparatus |
| EP3763945B1 (en) | 2018-06-11 | 2022-12-28 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Rotor and centrifugal compressor comprising rotor |
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| CN102365464A (en) * | 2009-07-13 | 2012-02-29 | 三菱重工业株式会社 | Impeller and rotary machine |
| CN102365464B (en) * | 2009-07-13 | 2014-10-29 | 三菱重工业株式会社 | impeller and rotary machine |
| US9404506B2 (en) | 2009-07-13 | 2016-08-02 | Mitsubishi Heavy Industries, Ltd. | Impeller and rotary machine |
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| CN1771397A (en) | 2006-05-10 |
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