CN106996391A - Impeller, centrifugal compressor and refrigerating circulatory device - Google Patents
Impeller, centrifugal compressor and refrigerating circulatory device Download PDFInfo
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- CN106996391A CN106996391A CN201611101833.2A CN201611101833A CN106996391A CN 106996391 A CN106996391 A CN 106996391A CN 201611101833 A CN201611101833 A CN 201611101833A CN 106996391 A CN106996391 A CN 106996391A
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- Prior art keywords
- impeller
- blade
- leading edge
- wheel hub
- edge portion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/04—Blade-carrying members, e.g. rotors for radial-flow machines or engines
- F01D5/043—Blade-carrying members, e.g. rotors for radial-flow machines or engines of the axial inlet- radial outlet, or vice versa, type
- F01D5/048—Form or construction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
- F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2240/00—Components
- F05D2240/20—Rotors
- F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
- F05D2240/307—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor related to the tip of a rotor blade
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/70—Shape
- F05D2250/71—Shape curved
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention provides impeller, centrifugal compressor and refrigerating circulatory device.The distribution of the speed of the fluid in interlobate stream is set suitably to change.The impeller of the disclosure possesses wheel hub and multiple blades.Blade has the main part of the leading edge portion of the top surface side positioned at wheel hub and the bottom surface side positioned at wheel hub.Opposite side in the side that connects with wheel hub, the front end of leading edge portion and the front end of main part extend from the top surface side of wheel hub towards bottom surface side.When overlooking blade from the radial direction vertical with the rotary shaft of impeller, the profile of the front end of leading edge portion is linear, and the profile of the front end of main part is curve-like.
Description
Technical field
This disclosure relates to impeller, centrifugal compressor and refrigerating circulatory device.
Background technology
Would be used for it is in the rotary part of centrifugal compressor, by fluid mainly on rolling tangential direction to suction
Accelerated the part referred to as impeller to fluid application kinetic energy.Impeller generally has the shape for being similar to the frustum of a cone, to link
The straight line at the center of the top surface of path and the center of the bottom surface in big footpath rotates for axle.As described in non-patent literature 1, leaf
Wheel is with the multiple blades (blade) radially configured.
Blade is collided in its leading edge to the fluid for being drawn into centrifugal compressor with certain angle.Because of the collision, in blade
Surface (suction surface) and the back side (pressure surface) between produce speed difference, to fluid apply kinetic energy.
Interval untill blade is from leading edge to trailing edge, because of the increase of the radius of turn of impeller, mainly and rolling tangential
The component velocity increase of the relevant fluid in direction.The increase in impeller with the position punishment speed of maximum outside diameter is maximum, can be determined
Surely the total amount of the kinetic energy of fluid is put on.
In addition, by with from the leading edge of blade towards trailing edge advance and between blade the area of section reduction in section side
Formula designs impeller, can prevent the speed reduction along the fluid on the direction on the surface of blade.
The speed of fluid in the inside (interlobate stream) of impeller is that the speed of the fluid on the surface of blade is depended on
For being equipped with the pressure ratio that the compressor of the impeller is tried to achieve.For example, the fluid that should be compressed be air, pressure ratio more than 4
Compressor in the case of, the speed (relative velocity) for the fluid observed in the leading edge of blade from blade reaches transonic speed.
In non-patent literature 1, the centrifugal compressor for target with pressure ratio 8 is recorded.In this case, the leading edge of blade is relatively fast
Spend for the high transonic speed of Mach number 1.2 or so.
Prior art literature
Patent document
Patent document 1：International Publication No. 2014/073377
Patent document 2：International Publication No. 2014/199498
Patent document 3：Japanese Unexamined Patent Publication 2011-117346 publications
Patent document 4：No. 2008/0229742 specification of U.S. Patent Application Publication No.
Non-patent literature
Non-patent literature 1：Colin Osborne et al. write,《AERODYNAMIC AND MECHANICAL DESIGN
OF AN 8：1PRESSURE RATIO CENTRIFUGAL COMPRESSOR》, NASA CR-134782, in April, 1975
The content of the invention
The flowing of fluid in the interlobate stream of impeller is extremely complex.Speed is produced in complicated flow field slow and high
The vortex (the high vortex of the vorticity of flowing) of intensity, kinetic energy is applied so can hinder from blade to fluid high-effective.In addition, because of whirlpool
The friction of fluid in stream and loss can be produced.This turns into the main cause of the decline of pressure ratio and adiabatic efficiency.
The disclosure with provide it is a kind of be used to making distribution appropriateization of the speed of fluid in interlobate stream and improve from
For the purpose of the technology of the efficiency of heart compressor.
That is, the disclosure provides a kind of impeller, and it is the impeller of centrifugal compressor, is possessed：
Wheel hub, it has top surface, bottom surface and outer peripheral face；With
It is fixed on the wheel hub and radially is arranged at multiple blades on the outer peripheral face of the wheel hub,
The blade has the master of the leading edge portion of the top surface side positioned at the wheel hub and the bottom surface side positioned at the wheel hub
Body portion,
In the side opposite with being fixed on the hub side of the blade, the front end of the leading edge portion and the main body
Partial front end extends from the top surface side of the wheel hub towards the bottom surface side,
When overlooking the blade from the radial direction vertical with the rotary shaft of the impeller, the leading edge portion it is described
The profile of front end is linear, and the profile of the front end of the main part is curve-like.
According to the disclosure, distribution appropriateization of the speed of the fluid in interlobate stream can be made and centrifugal compressed is improved
The efficiency of machine.
Brief description of the drawings
Fig. 1 is the sectional view of the centrifugal compressor of an embodiment of the disclosure.
Fig. 2 is the meridional projection figure of the impeller of the centrifugal compressor shown in Fig. 1.
Fig. 3 A are the schematically stereograms of the primary blades of impeller.
Fig. 3 B are the Partial enlarged side views of the primary blades of impeller.
Fig. 4 is the chart for the relation for representing blade angle β b and the distance away from leading edge.
Fig. 5 is the figure of the hub ratio for the impeller for representing the centrifugal compressor shown in Fig. 1.
Fig. 6 is the pie graph for the refrigerating circulatory device for having used the centrifugal compressor shown in Fig. 1.
Fig. 7 is the Partial enlarged side view of the primary blades of conventional impeller.
Embodiment
The present inventor analyzes the stream of the fluid (for example, vapor) in the inside (interlobate stream) of impeller in detail
It is dynamic.As a result, having found out following situations：Because large-scale vortex conflux with it is defeated and dispersed, cause to produce flowing in the inside of impeller stifled
The region (flowing very slow region) filled in.The present inventor attentively research confluxing of can suppressing to be vortexed on a large scale with it is defeated and dispersed
Blade shape, as a result, coming up with the impeller of the disclosure.
The impeller of 1st technical scheme of the disclosure is a kind of impeller of centrifugal compressor, is possessed：
Wheel hub, it has top surface, bottom surface and outer peripheral face；With
It is fixed on the wheel hub and radially is arranged at multiple blades on the outer peripheral face of the wheel hub,
The blade has the master of the leading edge portion of the top surface side positioned at the wheel hub and the bottom surface side positioned at the wheel hub
Body portion,
In the side opposite with being fixed on the hub side of the blade, the front end of the leading edge portion and the main body
Partial front end extends from the top surface side of the wheel hub towards the bottom surface side,
When overlooking the blade from the radial direction vertical with the rotary shaft of the impeller, the leading edge portion it is described
The profile of front end is linear, and the profile of the front end of the main part is curve-like.
Another performance of the impeller of 1st technical scheme of the disclosure, is a kind of impeller of centrifugal compressor, possesses：
Wheel hub, it has top surface, bottom surface and outer peripheral face；With
It is fixed on the wheel hub and radially is arranged at multiple blades on the outer peripheral face of the wheel hub,
The blade has the master of the leading edge portion of the top surface side positioned at the wheel hub and the bottom surface side positioned at the wheel hub
Body portion,
The leading edge portion includes leading edge, and the leading edge constitutes the leaf on the direction parallel with the rotary shaft of the impeller
One end of piece,
The front end of the leading edge portion and the front end of the main part are described from the top surface side direction of the wheel hub
Bottom surface side extends,
The front end of the leading edge portion and the front end of the main part constitute the rotary shaft with the impeller
One end of the blade on vertical radial direction, the other end in the opposite side positioned at described one end, the blade is fixed
In the wheel hub,
When overlooking the blade from the radial direction, the profile of the front end of the leading edge portion be it is linear,
The profile of the front end of the main part is curve-like.
According to the impeller of the 1st technical scheme, in the inside (interlobate stream) of impeller, even if because of the stripping in boundary layer
And/or the leakage current at blade end produces the vortex of high intensity, can also suppress confluxing and large-scale for above-mentioned vortex.In other words,
The distribution of the speed of the fluid in interlobate stream can be made suitably to change.As a result, the blocking during the inside of impeller can be suppressed
And flow with making smooth fluid, it can efficiently apply kinetic energy from blade to fluid.Especially, according to the 1st technical scheme, even if
Under low reynolds number and the operating condition of low specific-speed, the performance of compressor is also able to maintain that.As long as using the leaf of the 1st technical scheme
Wheel, it becomes possible to expeditiously compress low-density and highly viscous fluid (for example, vapor).
In the 2nd technical scheme of the disclosure, for example, the blade of the impeller of the 1st technical scheme include pressure surface and
Suction surface, the profile of the front end of leading edge portion when overlooking the blade from the radial direction includes the malleation
1st upstream portion of surface side and the 2nd upstream portion of the negative pressure surface side, the 1st upstream portion and the 2nd upstream portion
Both sides are linear, and the profile of the front end of main part when overlooking the blade from the radial direction includes institute
State under the 1st downstream part of malleation surface side and the 2nd downstream part of the negative pressure surface side, the 1st downstream part and the described 2nd
Trip part both sides are curve-like.According to such construction, the effect in the 1st technical scheme can be effectively obtained.
In the 3rd technical scheme of the disclosure, for example, by by the blade rotation be projected on the 1st technical scheme or
In meridional projection figure obtained from the meridian plane comprising the rotary shaft of the impeller of 2nd technical scheme, will be parallel to institute
When the total length of the blade in the axial direction for the rotary shaft for stating impeller is defined as meridian plane length, the leading edge portion is in institute
State and occupied in meridional projection figure from the position of the leading edge of the blade to towards the meridian plane length of axially advancing
Untill 5% position.As long as the scope to leading edge portion is limited to a certain degree, it becomes possible to avoid the curtailment of blade,
So enough energy can be applied to fluid.
In the 4th technical scheme of the disclosure, for example, the 1st technical scheme~the 3rd any technical scheme in technical scheme
The multiple blade of impeller each constitute the primary blades of the impeller, the impeller is also equipped with multiple back blades, described many
Individual back blades is respectively arranged in the circumference of the impeller between the primary blades adjacent to each other and the primary blades.Consider
The critical cross-section area (minimum cross-sectional area of interlobate stream) that maximum stream flow according to required by centrifugal compressor is tried to achieve,
Back blades with shape obtained from cut-out primary blades can be set.According to the 4th technical scheme, it can construct with broader
The centrifugal compressor of range of flow.
In the 5th technical scheme of the disclosure, for example, any technical side in the technical scheme of the 1st technical scheme~the 4th
At the position of the leading edge of the blade of the impeller of case, the ratio of radius of the radius relative to the blade of the wheel hub
In 0.6~0.7 scope.According to the 5th technical scheme, it can effectively suppress the upset in flow field and improve pressure ratio.
The centrifugal compressor of 6th technical scheme of the disclosure is that possess any in the technical scheme of the 1st technical scheme~the 5th
The centrifugal compressor of the impeller of technical scheme and the shield wall of the receiving impeller.According to the 6th technical scheme, using the teaching of the invention it is possible to provide efficiently
The centrifugal compressor of rate.
The refrigerating circulatory device of 7th technical scheme of the disclosure is that possess the centrifugal compressor of the 6th technical scheme and use
Saturated vapour pressure under normal temperature is that the material of negative pressure is used as the device of refrigerant.According to the 7th technical scheme, can efficiently it improve
The pressure of refrigerant, so the efficiency of refrigerating circulatory device can be improved.
In the 8th technical scheme of the disclosure, for example, the material of the kind of refrigeration cycle of the 7th technical scheme includes water.Make
Being applied to efficiently compression with the centrifugal compressor of the impeller of the disclosure includes the refrigerant of water (vapor).
Hereinafter, embodiment of this disclosure is illustrated referring to the drawings.The disclosure is not limited to following embodiment.
As shown in figure 1, the centrifugal compressor 100 of present embodiment possesses：Axle 11, impeller 2, backboard 13 and housing 15.
Impeller 2 is fixed on axle 11.Backboard 13 is configured at the dorsal part of impeller 2.Impeller 2 is contained in housing 15.Centrifugal compressor 100 is by axle 11
Rotation and drive, compression work fluid.In addition, in the following description, sometimes also will be parallel with the rotary shaft O of impeller 2
The face side of backboard 13 in direction (axial direction) is referred to as front, by its rear side referred to as rear.
Impeller 2 has：Wheel hub 20, (the full blade of multiple primary blades 21：Whole lamina) and multiple back blades 22
(splitter blade：Splitterr vanes).Wheel hub 20 has the top surface 20p of path and the bottom surface 20q in big footpath in the axial direction, along
Rotary shaft O is smoothly expanding from top surface 20p towards bottom surface 20q.Primary blades 21 and back blades 22 are fixed on wheel hub 20, radially
Ground is arranged on the outer peripheral face of wheel hub 20.Primary blades 21 and back blades 22 are alternately arranged in the circumference of impeller 2.Back blades 22
It is the blade shorter than primary blades 21.
In addition, what back blades 22 was not required, it is convenient to omit.
Housing 15 has：Shield wall 3, perimeter component 17 and forepiece 18.Shield wall 3 has the shape along impeller 2.
Shield wall 3 extends and forms suction inlet 12 forwards than impeller 2.Perimeter component 17 forms vortex chamber 16 around impeller 2, should
Vortex chamber 16 is connected with the diffuser being formed between backboard 13 and shield wall 3.
Fig. 2 is by the rotation projection of the meridian plane comprising rotary shaft O primary blades 21, back blades 22 and the shield to impeller 2
Meridional projection figure (revolved projection) obtained from cover wall 3.The neck of shape shown by meridional projection figure in turbomachinery
Domain is referred to as " meridian plane shape ".In this manual, the outer peripheral edge of the primary blades 21 in face of suction inlet 12 is defined as primary blades
21 leading edge 31.The front end 32 of primary blades 21 will be defined as in face of the outer peripheral edge of the primary blades 21 of shield wall 3.Equally, it will face
The outer peripheral edge of the back blades 22 of suction inlet 12 is defined as the leading edge 41 of back blades 22.By in face of the outer of the back blades 22 of shield wall 3
Periphery is defined as the front end 42 of back blades 22.Leading edge 31 and leading edge 41 are presented axially in the top surface 20p identicals with wheel hub 20
Side.In the present embodiment, the leading edge 31 of primary blades 21 is parallel to the direction vertical with the rotary shaft O of impeller 2.Back blades 22
Trailing edge 43 be located at the identical position of trailing edge 33 with primary blades 21.The leading edge 41 of back blades 22 is located at the leading edge than primary blades 21
31 position rearward.Leading edge 31 constitutes one end of the primary blades 21 on the direction parallel with the rotary shaft of impeller 2.
As shown in Figure 3A, primary blades 21 have positioned at the leading edge portion 24 of the top surface 20p sides of wheel hub 20 and positioned at wheel hub 20
Bottom surface 20q sides main part 25.Main part 25 is smoothly connected with leading edge portion 24.In primary blades 21 with being fixed on
The opposite side in the side of wheel hub 20, the front end 35 of leading edge portion 24 and the front end 36 of main part 25 are from the top surface 20p sides of wheel hub 20
Towards the extension of bottom surface 20q sides.As shown in Figure 3 B, primary blades 21 are overlooked from the radial direction vertical with the rotary shaft O of impeller 2
When, the profile of the front end 35 of leading edge portion 24 is linear, and the profile of the front end 36 of main part 25 is curve-like.Wheel hub 20 with
The fillet 37 of primary blades 21 is overall curvilinear from leading edge 31 to trailing edge 33.In figure 3b, rotary shaft O passes through linear
The border of leading edge portion 24 and curvilinear main part 25.Leading edge portion 24 includes leading edge 31.The front end 35 of leading edge portion 24
One end of the primary blades 21 on the radial direction vertical with the rotary shaft of impeller 2 is constituted with the front end 36 of main part 25, in place
The other end in the opposite side of one end, primary blades 21 are fixed on wheel hub 20.
As shown in Figure 3 B, primary blades 21 have pressure surface 21p and suction surface 21q.The primary blades of the direction of rotation side of impeller 2
21 surface is pressure surface 21p (pressurized plane), and the surface of the primary blades 21 of the side opposite with pressure surface 21p is suction surface 21q
(non-pressurised face).Equally, the surface of the back blades 22 of the direction of rotation side of impeller 2 is the pair of pressure surface, in contrast to this side
The surface of blade 22 is suction surface.
The impeller for being recorded in patent document 1~4 assumes that in reynolds number Re be 106Used under conditions of left and right.Specifically,
It is assumed that：As using air as working fluid booster or gas turbine prime movers key element centrifugal compressor.
Reynolds number Re is represented by following formula (1).
ρ：The density of working fluid (during suction)
R1T：The radius of the shield of the leading edge of blade
W1T：The shroud relative velocity of the leading edge of blade
ν：The kinematic viscosity of working fluid (during suction)
In addition, in patent document 1~4, it is assumed that be：It is design as 0.6~0.8 or so than fast Ns.It is than fast Ns
The index of the size of fluid machinery is represented, is represented by following formula (2).
Ns=(NQ1/2)/(H4)1/3…(2)
N：The rotating speed [rpm] of axle
Q：Volume flow (entrance) [m of working fluid3/sec]
H：Heat drop (head：head)[m]
On the other hand, sometimes will be compressible beyond air in the centrifugal compressor for being used in conditioner etc.
Property fluid is used as working fluid.Because of the decline of the viscosity of working fluid, Re can drop to 10 sometimes4Left and right.In the situation
Under, problem can be turned into by coming from the multiple of vortex of the high intensity on the surface of wheel hub and the surface of blade.Because of the vortex of high intensity
Mutually influence, large-scale upset can occur in the inside of impeller.As a result, the performance of centrifugal compressor significantly under
Drop.
As shown in fig. 7, in the blade 210 of conventional impeller, the front end 210a of malleation surface side profile and negative pressure surface side
Front end 210b profile it is all overall curvilinear.Therefore, it can be accelerated immediately with the leading edge 210c fluids collided.In the situation
Under, because the vortex of high intensity is mutually influenced, large-scale upset easily occurs in the inside of impeller.
On the other hand, in the impeller 2 of present embodiment, primary blades 21 have leading edge portion 24.Before leading edge portion 24
The profile at end 35 is linear, so fluid is not easy to be accelerated in leading edge portion 24.As a result, the hypertrophy in boundary layer can be suppressed
Change, the generation position of the vortex of low energy and high intensity caused by the stripping in boundary layer is moved compared with conventional blade 210 (Fig. 7)
Downstream side.Downstream is shifted to by the generation position of vortex, the surface beyond the surface of primary blades 21 be (wheel hub 20
Outer peripheral face) low energy as caused by the stripping in boundary layer vortex in the neighbouring generation of leading edge 31, the generation position of vortex can also be produced
Raw skew.Cause inside (interlobate stream) production in impeller 2 with defeated and dispersed thereby, it is possible to suppress to conflux because of large-scale vortex
This case that the region that raw flowing is plugged.In other words, the distribution of the speed of fluid in interlobate stream can be made appropriate
Change.The effect is 104In the flow field of the low reynolds number of left and right substantially.
In addition, in leading edge portion 24, suction surface 21q sides, which turn into slow down, to be flowed, pressure surface 21p sides, which turn into, to be accelerated to flow.
It is decelerated in suction surface 21q flowings, so the hypertrophyization in boundary layer and the stripping in boundary layer can be suppressed.Added in pressure surface flowing
Speed, so low energy stream caused by the stripping borderline layer by the suction surface 21q generations in adjacent primary blades 21 can be blown away.Can
Low energy stream is prevented to be attached to pressure surface 21p, and the suction surface 21q of the primary blades 21 with peeling off source is collided again.Thus, it can suppress
The VELOCITY DISTRIBUTION of fluid caused by the Secondary Flow of the primary blades 21 adjacent because coming from the pressure surface 21p of primary blades 21 is disturbed
Disorderly, velocity flow profile can be made suitably to change.
As shown in Figure 3 B, the profile of the front end 35 of the leading edge portion 24 when overlooking primary blades 21 from radial direction includes malleation
1st upstream portion 35a of face 21p sides and the 2nd upstream portion 35b of suction surface 21q sides.1st upstream portion 35a and the 2nd upstream
Part 35b both sides are linear.In addition, from radial direction overlook primary blades 21 when main part 25 front end 36 profile bag
Include the 1st downstream part 36a of pressure surface 21p sides and the 2nd downstream part 36b of suction surface 21q sides.1st downstream part 36a and
2 downstream part 36b both sides are curve-like.1st downstream part 36a and the 2nd downstream part 36b, which have towards suction surface 21q sides, to be turned into
Convex curvature.According to such construction, above-mentioned effect can be effectively obtained.
As shown in Fig. 2 the total length parallel to the primary blades 21 in the rotary shaft O of impeller 2 axial direction is defined as into meridian plane
Length L.In Fig. 2 meridional projection figure, leading edge portion 24 is occupied from the position of the leading edge 31 of primary blades 21 to towards axially
Untill traveling meridian plane length L 5% position.Main part 25 is occupied from meridian plane length L 5% position to primary blades
Untill the position of 21 trailing edge 33.In addition, in Fig. 3 A and Fig. 3 B, leading edge portion 24 is large shown.If to leading edge portion
24 scope is limited to a certain degree, then can avoid the curtailment of primary blades 21, so can apply enough to fluid
Energy.
If as shown in figure 4, being conceived to the blade angle β b of the blade (primary blades) for the side that connects with wheel hub 20, from leading edge
The position (100%) of trailing edge is arrived in position (0%), in the blade angle β b and conventional blade of the blade (primary blades 21) of the disclosure
Blade angle β b between not can be appreciated that big difference.On the other hand, it is fixed on hub side with blade (primary blades) if being conceived to
The blade angle β b of the blade (primary blades) of opposite side (shroud), then the disclosure blade (primary blades 21) blade
There is big difference between angle beta b and the blade angle β b of conventional blade.That is, the primary blades 21 of the disclosure have front end 35
Profile be linear leading edge portion 24, so untill predetermined position (5%), being shown from the position of leading edge (0%)
Absolute value very big blade angle β b.
As shown in figure 5, the impeller 2 of present embodiment has 0.6~0.7 hub ratio (D1/D2)." hub ratio " is finger wheel
Ratios (D1/D2) of the radius D1 of hub 20 relative to the radius D2 of the primary blades 21 at the position of the leading edge 31 of primary blades 21.If
Hub ratio is in scope as described above, then can obtain effect as described below.
The impeller of the centrifugal compressor of common design has 0.4~0.5 or so hub ratio.Such as present embodiment that
When hub ratio to be set in sample 0.6~0.7 scope, the inflow velocity increase of the fluid flowed into impeller 2 easily improves pressure
Than.But, the upset in flow field and the thus decline of caused performance also easily show.Therefore, by with 0.6~0.7
Hub ratio impeller in use the primary blades 21 of the construction illustrated with reference picture 3A and Fig. 3 B, can effectively suppress stream
The upset of field simultaneously improves pressure ratio.Especially, when high speed rotates, it can prevent that referred to as impeller blocks (inducer
Choking), the blocking of the vicinity of leading edge 31 in primary blades 21.As a result, high-pressure ratio and wide operating range can be constructed
Centrifugal compressor.
(embodiment of refrigerating circulatory device)
As shown in fig. 6, the refrigerating circulatory device 200 of present embodiment possesses：Make major loop 6, the heat absorption of refrigerant circulation
1st circulation road 7 and the 2nd circulation road 8 of heat transmission.In the circulation road 8 of the circulation of major loop the 6, the 1st road 7 and the 2nd, fill out
Fill the refrigerant for liquid under normal temperature.Specifically, as refrigerant, normal temperature (JIS can be used：20℃±15
DEG C/JIS Z8703) under saturated vapour pressure be negative pressure refrigerant.As such refrigerant, it can enumerate with water or alcohols
For the refrigerant of main component.When refrigerating circulatory device 200 is operated, in the circulation road 8 of the circulation of major loop the 6, the 1st road 7 and the 2nd
As the negative pressure state forced down than air.In this manual, " main component " refers to include most compositions on mass ratio.
Major loop 6 includes：Evaporator 66, the 1st compressor 61, intercooler 62, the 2nd compressor 63, condenser 64 with
And expansion valve 65, these equipment are by stream by said sequence connection.
The storing refrigerant liquid of evaporator 66 and evaporate refrigerant liquid inside it.Specifically, it is stored in evaporator
66 refrigerant liquid is circulated by the 1st circulation road 7 via heat absorption heat exchanger 71.For example, refrigerating circulatory device 200 be into
In the case of the indoor conditioner for letting cool gas of row, heat absorption heat exchanger 71 is arranged at interior, makes to be supplied by air blower
The indoor air given is cooled down by the heat exchange with refrigerant liquid.
1st compressor 61 and the 2nd compressor 63 compress refrigerant vapour with two benches., can be with as the 1st compressor 61
Use the centrifugal compressor 100 foregoing described.2nd compressor 63 can both be independently of the positive displacement pressure of the 1st compressor 61
Contracting machine or by the compressor 61 of axle 11 and the 1st link centrifugal compressor (for example, the centrifugal compressed foregoing described
Machine 100).The motor 67 for rotating axle 11 can be both configured between the 1st compressor 61 and the 2nd compressor 63, can also be matched somebody with somebody
It is placed in the outside of any compressor.As long as making the 1st compressor 61 link with the 2nd compressor 63 by axle 11, it becomes possible to reduce the 1st
The part number of packages of the compressor 63 of compressor 61 and the 2nd.
Intercooler 62 make from the 1st compressor 61 discharge refrigerant vapour before the 2nd compressor 63 is drawn into it is cold
But.Intercooler 62 both can be the heat exchanger of direct contact type or the heat exchanger of indirect type.
Condenser 64 makes refrigerant vapour condense and storing refrigerant liquid inside it.Specifically, it is stored in condensation
The refrigerant liquid of device 64 is circulated by the 2nd circulation road 8 via heat transmission heat exchanger 81.For example, being in refrigerating circulatory device 200
In the case of carrying out the indoor conditioner for letting cool gas, heat transmission heat exchanger 81 is arranged at outdoor, makes by air blower
The outdoor air of supply is heated by the heat exchange with refrigerant liquid.
But, refrigerating circulatory device 200 must be not necessarily the special conditioner of cold air.As long as example, making to set
1st heat exchanger disposed within and it is arranged at the 2nd heat exchanger of outdoor and each via four-way valve and evaporator 66 and condenses
Device 64 is connected, it becomes possible to obtain the conditioner that changeable cold air operation is operated with heating.In this case, the 1st heat is handed over
Parallel operation and the 2nd heat exchanger both sides as heat absorption with heat exchanger 71 and heat transmission heat exchanger 81 function.In addition, system
SAPMAC method device 200 must be not necessarily conditioner, for example, can also be cold.Moreover, heat absorption heat exchanger 71
Cooling object and the heating target of heat transmission heat exchanger 81 can also be gas or liquid beyond air.
Expansion valve 65 is one of the mechanism of decompressor depressurized to chilled refrigerant liquid.But, as negative booster
Structure, for example, can also be not provided with expansion valve 65, but use the liquid level of the refrigerant liquid made in evaporator 66 than cold in major loop 6
The high such composition of the liquid level of refrigerant liquid in condenser 64.
Evaporator 66 must be not necessarily the heat exchanger of direct contact type or the heat exchanger of indirect type.
In this case, the thermal medium being cooled in evaporator 66 is circulated on the 1st circulation road 7.Equally, condenser 64 is not necessarily necessary
It is the heat exchanger of direct contact type or the heat exchanger of indirect type.In this case, it is heated in condenser 64
Thermal medium circulated on the 2nd circulation road 8.
For the refrigerating circulatory device 200 of present embodiment, in the case where using water as refrigerant, the 1st compressor
61 and the 2nd compressor 63 is compressed to the vapor of negative pressure.The centrifugal compressor 100 foregoing described is applied to as water steams
The purposes that the such low-density of gas and highly viscous fluid are compressed.In addition, refrigerating circulatory device 200 can be relative to required
Pressure ratio for fluid flow it is small in the case of i.e. under conditions of low reynolds number and low specific-speed operate.Therefore, said before
Clear centrifugal compressor 100 is applied to the refrigerating circulatory device 200 of present embodiment.
Industrial utilizability
According to technology disclosed in this specification, under low reynolds number and the operating condition of low specific-speed, pressure is also able to maintain that
The performance of contracting machine.Technology disclosed in this specification has been suitable for use with the refrigerating circulatory device of the natural refrigerants such as vapor.
According to technology disclosed in this specification, enable in particular to improve the performance of the refrigerating circulatory device of small output, and can reduce
The maintenance frequency of refrigerating circulatory device.
Description of reference numerals
2：Impeller；
20：Wheel hub；
20p：The top surface of wheel hub；
20q：The bottom surface of wheel hub；
21：Primary blades；
21p：Pressure surface；
21q：Suction surface；
22：Back blades；
24：Leading edge portion；
25：Main part；
31：Leading edge；
32：Front end；
35：The front end of leading edge portion；
35a：1st upstream portion of the profile of the front end of leading edge portion；
35b：2nd upstream portion of the profile of the front end of leading edge portion；
36a：1st downstream part of the profile of the front end of main part；
36b：2nd downstream part of the profile of the front end of main part；
36：The front end of main part；
100：Centrifugal compressor；
200：Refrigerating circulatory device；
O：The rotary shaft of impeller.
Claims (8)
1. a kind of impeller, is the impeller of centrifugal compressor, possesses：
Wheel hub with top surface, bottom surface and outer peripheral face；With
It is fixed on the wheel hub and radially is arranged at multiple blades on the outer peripheral face of the wheel hub,
The blade has the main part of the leading edge portion of the top surface side positioned at the wheel hub and the bottom surface side positioned at the wheel hub
Point,
In the side opposite with being fixed on the hub side of the blade, the front end of the leading edge portion and the main part
Front end extend from the top surface side of the wheel hub towards the bottom surface side,
When overlooking the blade from the radial direction of the rotary shaft perpendicular to the impeller, the front end of the leading edge portion
Profile be linear, the profile of the front end of the main part is curve-like.
2. impeller according to claim 1,
The blade includes pressure surface and suction surface,
The profile of the front end of leading edge portion when overlooking the blade from the radial direction, including the pressure surface
1st upstream portion of side and the 2nd upstream portion of the negative pressure surface side, the 1st upstream portion and the 2nd upstream portion are double
Side be it is linear,
The profile of the front end of main part when overlooking the blade from the radial direction, including the pressure surface
1st downstream part of side and the 2nd downstream part of the negative pressure surface side, the 1st downstream part and the 2nd downstream part are double
Side is curve-like.
3. impeller according to claim 1,
The meridian plane obtained from by the way that blade rotation is projected on into the meridian plane comprising the rotary shaft of the impeller
It is long the total length parallel to the blade in the axial direction of the rotary shaft of the impeller is defined as into meridian plane in perspective view
When spending,
The leading edge portion, in the meridional projection figure, is occupied from the position of the leading edge of the blade to towards the axle
Untill 5% position of the meridian plane length of advancing.
4. impeller according to claim 1,
The multiple blade each constitutes the primary blades of the impeller,
The impeller is also equipped with multiple back blades,
The multiple back blades is respectively arranged at the primary blades adjacent to each other in the circumference of the impeller and the main lobe
Between piece.
5. impeller according to claim 1,
At the position of the leading edge of the blade, the ratio of radius of the radius relative to the blade of the wheel hub is in
0.6~0.7 scope.
6. a kind of centrifugal compressor, possesses：
Impeller according to any one of claims 1 to 5；With
Accommodate the shield wall of the impeller.
7. a kind of refrigerating circulatory device,
Possess the centrifugal compressor described in claim 6,
And it is the material of negative pressure as refrigerant to use saturated vapour pressure under normal temperature.
8. refrigerating circulatory device according to claim 7,
The material includes water.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016-011785 | 2016-01-25 | ||
| JP2016011785 | 2016-01-25 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106996391A true CN106996391A (en) | 2017-08-01 |
Family
ID=57850964
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201611101833.2A Pending CN106996391A (en) | 2016-01-25 | 2016-12-05 | Impeller, centrifugal compressor and refrigerating circulatory device |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20170211584A1 (en) |
| EP (1) | EP3196476A1 (en) |
| JP (1) | JP2017133498A (en) |
| CN (1) | CN106996391A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107989823A (en) * | 2017-12-26 | 2018-05-04 | 北京伯肯节能科技股份有限公司 | Impeller, centrifugal compressor and fuel cell system |
| CN109184804A (en) * | 2018-11-02 | 2019-01-11 | 北京控制工程研究所 | A kind of turbo wheel of space Brayton Cycle system |
| CN111655385A (en) * | 2018-02-05 | 2020-09-11 | 富士胶片株式会社 | Method for manufacturing recording medium and image recording method |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102017215085A1 (en) * | 2017-08-29 | 2019-02-28 | Efficient Energy Gmbh | Heat pump with a cooling device for cooling a Leitraums or a suction mouth |
| US11286779B2 (en) | 2020-06-03 | 2022-03-29 | Honeywell International Inc. | Characteristic distribution for rotor blade of booster rotor |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB594538A (en) * | 1944-09-18 | 1947-11-13 | British Thomson Houston Co Ltd | Improvements in centrifugal type impellers for compressors and the like |
| GB210353A (en) * | 1923-01-31 | 1924-01-31 | Erste Bruenner Maschinen-Fabriks-Gesellschaft | |
| FR2230229A5 (en) * | 1973-05-16 | 1974-12-13 | Onera (Off Nat Aerospatiale) | |
| US20080229742A1 (en) | 2007-03-21 | 2008-09-25 | Philippe Renaud | Extended Leading-Edge Compressor Wheel |
| JP5308319B2 (en) | 2009-12-02 | 2013-10-09 | 三菱重工業株式会社 | Centrifugal compressor impeller |
| GB201122142D0 (en) * | 2011-12-21 | 2012-02-01 | Venus Systems Ltd | Centrifugal compressors |
| JP5611307B2 (en) | 2012-11-06 | 2014-10-22 | 三菱重工業株式会社 | Centrifugal rotating machine impeller, centrifugal rotating machine |
| EP3009686B1 (en) | 2013-06-13 | 2017-11-15 | Mitsubishi Heavy Industries, Ltd. | Impeller and fluid machine |
| CN204312394U (en) * | 2014-11-13 | 2015-05-06 | 湖南天雁机械有限责任公司 | With the turbosupercharger of diagonal impeller of compressor |
-
2016
- 2016-12-05 CN CN201611101833.2A patent/CN106996391A/en active Pending
- 2016-12-15 JP JP2016242981A patent/JP2017133498A/en active Pending
-
2017
- 2017-01-19 EP EP17152121.4A patent/EP3196476A1/en not_active Withdrawn
- 2017-01-20 US US15/411,885 patent/US20170211584A1/en not_active Abandoned
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107989823A (en) * | 2017-12-26 | 2018-05-04 | 北京伯肯节能科技股份有限公司 | Impeller, centrifugal compressor and fuel cell system |
| CN107989823B (en) * | 2017-12-26 | 2023-12-01 | 北京伯肯节能科技股份有限公司 | Impeller, centrifugal compressor, and fuel cell system |
| CN111655385A (en) * | 2018-02-05 | 2020-09-11 | 富士胶片株式会社 | Method for manufacturing recording medium and image recording method |
| US11433686B2 (en) | 2018-02-05 | 2022-09-06 | Fujifilm Corporation | Method of producing recording medium and image recording method |
| CN109184804A (en) * | 2018-11-02 | 2019-01-11 | 北京控制工程研究所 | A kind of turbo wheel of space Brayton Cycle system |
| CN109184804B (en) * | 2018-11-02 | 2021-04-13 | 北京控制工程研究所 | Turbine impeller for space Brayton cycle system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017133498A (en) | 2017-08-03 |
| EP3196476A1 (en) | 2017-07-26 |
| US20170211584A1 (en) | 2017-07-27 |
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Application publication date: 20170801 |