CN107002705B - Impeller and rotating machinery - Google Patents
Impeller and rotating machinery Download PDFInfo
- Publication number
- CN107002705B CN107002705B CN201580065062.3A CN201580065062A CN107002705B CN 107002705 B CN107002705 B CN 107002705B CN 201580065062 A CN201580065062 A CN 201580065062A CN 107002705 B CN107002705 B CN 107002705B
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- Prior art keywords
- impeller
- reinforcing ring
- impeller bodies
- bodies
- back side
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Classifications
-
- 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
- F04D29/02—Selection of particular materials
- F04D29/023—Selection of particular materials especially adapted for elastic fluid pumps
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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
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
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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
- F04D29/26—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
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- 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
- F05D2300/00—Materials; Properties thereof
- F05D2300/60—Properties or characteristics given to material by treatment or manufacturing
- F05D2300/603—Composites; e.g. fibre-reinforced
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention provides a kind of impeller and rotating machinery.The impeller has: impeller bodies (31) are formed by resin and in the form of annular discs, are rotated together with centered on axis (O) with rotary shaft (2)；Compressor blade (25), the wheel hub surface (31a) in impeller bodies (31) are provided with multiple；And reinforcing ring (41), it is embedded in the back side (32) for being formed in impeller bodies (31) from peripheral side and there is the stepped part (36) towards the chimeric surface (37) of peripheral side, and is formed by resin and reinforcing fiber and circumferentially annularly.
Description
Technical field
The present invention relates to a kind of impeller for being set to rotating machinery and the rotating machineries for having impeller.
This application claims excellent at Japanese patent application 2014-245157 of Japanese publication based on December 3rd, 2014
It first weighs, its contents are hereby incorporated herein by reference.
Background technique
In the global sexual development of earth environmental protection, for example, it is relevant to exhaust, the oil consumption of internal combustion engines such as the engine of automobile
Limitation is constantly reinforced.Turbocharger is that compressed air is sent into engine and makes the rotating machinery of fuel combustion, with nature
The engine of air-breathing, which is compared, can improve oil consumption and raising CO2The effect of reduction.
In turbocharger, turbine carries out rotation driving by the exhaust of engine, thus makes the impeller of centrifugal compressor
Rotation.It is decelerated and is boosted through diffuser by the rotation compressed air of impeller, and supplied via vortex stream road to hair
Motivation.In addition, the driving method as turbocharger, in addition to by exhaust driven in the way of other than, it is known that it is for example sharp
Driving method with motor and the driving method etc. using prime mover.
Impeller as turbocharger, it is known that such as it is described in Patent Document 1 using carbon fibre reinforced plastic conjunction
Impeller made of composite material (hereinafter referred to as resin) at resin.Here, the impeller of this resin is compared with the impeller of metal
Rigidity is lower, and deflection becomes larger due to the influence of centrifugal force when rotation.Therefore, the diameter of the boss hole chimeric with rotary shaft expands
Greatly, it is possible to damage spin balancing.
In view of this problem, in impeller described in Patent Document 1, metal ring is arranged by overleaf portion, it is suppressed that
The deformation of the impeller as caused by centrifugal force.
Conventional art document
Patent document
Patent document 1: Japanese Patent Publication 3-10040 bulletin
Summary of the invention
The invention technical task to be solved
As disclosed in patent document 1, when using metal ring, since impeller is formed by resin, impeller and ring
Material is different.Therefore, the linear expansion coefficient of metal ring becomes bigger than the linear expansion coefficient of the impeller of resin system, according to
Service condition, can not be by the stress distribution generated in impeller to ring, it is possible to can not inhibit the deformation of impeller.Also, metal
Density ratio resin is high, therefore ring itself enlarged-diameter due to the influence of centrifugal force, can not inhibit the deformation of impeller, it is difficult to ensure leaf
The reliability of wheel.
The present invention provides a kind of impeller and rotating machinery that can also ensure that reliability even with resin material.
For solving the means of technical task
First method according to the present invention, impeller have: impeller bodies are formed by resin and in the form of annular discs, in rotation
It is rotated together with centered on mandrel with rotary shaft；Blade is provided with multiple in the front side of the impeller bodies；And reinforcing ring, from
Peripheral side is embedded in the back side for being formed in the impeller bodies and has the stepped part towards the face of peripheral side, and by resin and
Reinforcing fiber forms and along the circumferential annular in shape of the impeller bodies.
According to this impeller, reinforcing ring is formed by resin and reinforcing fiber, thus the material of impeller bodies and reinforcing ring
Material is roughly the same.Therefore, the difference of the linear expansion coefficient of impeller bodies and reinforcing ring becomes smaller, and is able to suppress because thermal expansion causes
Reinforcing ring enlarged-diameter caused by impeller bodies restraining force decline.In addition, resin density is lower, therefore it is able to suppress
The restraining force decline of impeller bodies caused by the enlarged-diameter of reinforcing ring due to centrifugal force.Also, reinforcing ring includes reinforcing fiber,
Thus, it is possible to improve rigidity, reinforcing ring itself is able to suppress because of the pact of impeller bodies caused by enlarged-diameter caused by centrifugal force
Beam force decline.Therefore, the centrifugal force that can will act on impeller bodies is assigned to reinforcing ring, can reduce because of centrifugal force generation
The stress of impeller bodies is able to suppress the deformation of impeller entirety.
Second method according to the present invention, the stepped part of above-mentioned first method can be formed in from the Pivot axle
Position until 2/3 of the diameter dimension between the Pivot axle and the outer circumference end of the impeller bodies.
It, can be in the radial dimension of of the central axis from impeller bodies to impeller bodies by forming stepped part in this position
Reinforcing ring is arranged in 2/3 position.By the way that reinforcing ring is arranged in this position, the leaf generated by centrifugal force can be more effectively reduced
The stress of wheel body is able to suppress the deformation of impeller entirety.
The stepped part of Third Way according to the present invention, above-mentioned first method can be formed as follows, that is, institute
The radial center for stating reinforcing ring is located at from the outer of the Pivot axle to more than the Pivot axle and the impeller bodies
0.1 times of diameter dimension between Zhou Duan and it is less than the position of the diameter dimension.
By forming stepped part in this position, answering for the impeller bodies generated by centrifugal force can be more effectively reduced
Power is able to suppress the deformation of impeller entirety.
Fourth way according to the present invention can be equipped with prominent from the back side in the impeller bodies of above-mentioned first method
And the boss portion chimeric with the rotary shaft, the stepped part are formed in the boss portion.
According to aforesaid way, reinforcing ring is equipped in the boss portion for being set to impeller bodies.Thereby, it is possible to reduce in boss portion
Because centrifugal force generate stress, be able to suppress the deformation of impeller entirety.
5th mode according to the present invention, the radial width dimensions of the reinforcing ring of above-mentioned first to fourth mode with
The circumferential wing thickness size of the blade is identical, and the thickness in the direction of the Pivot axle of the reinforcing ring is greater than institute
State the radial width dimensions of reinforcing ring.
By forming reinforcing ring with this size, answering for the impeller bodies generated by centrifugal force can be more effectively reduced
Power is able to suppress the deformation of impeller entirety.
6th mode according to the present invention, in the reinforcing ring of the above-mentioned first to the 5th mode, the reinforcing fiber can
It is configured to the circumferentially extending along the impeller bodies.
If centrifugal force acts on reinforcing ring, generation acts on drawing force in the circumferential.Therefore, reinforcing fiber is along the drawing force
The direction of effect i.e. circumferentially extend, thus, it is possible to inhibit because of this drawing force caused by reinforcing ring itself deformation.Therefore, can
Inhibit the restraining force decline of impeller bodies, the centrifugal force that can will act on impeller bodies is assigned to reinforcing ring.Therefore, can subtract
The stress of few impeller bodies, is able to suppress the deformation of impeller entirety.
7th mode according to the present invention, impeller have: impeller bodies, discoid in what is be formed by resin, in rotation
It is rotated together with centered on mandrel with rotary shaft；Blade is provided with multiple in the front side of the impeller bodies；And reinforcing ring, from
Peripheral side is set to the back side for being formed in the impeller bodies and has the stepped part towards the face of peripheral side, and only by strengthening
Fiber forms and along the circumferential annular in shape of the impeller bodies.
According to this impeller, reinforcing ring is only formed by reinforcing fiber, thus the linear expansion system of impeller bodies and reinforcing ring
Several differences become smaller, caused by being able to suppress because of thermal expansion caused by the enlarged-diameter of reinforcing ring under the restraining force of impeller bodies
Drop.Also, carbon fiber density is lower, therefore is able to suppress the impeller bodies caused by the enlarged-diameter of reinforcing ring due to centrifugal force
Restraining force decline.Therefore, the centrifugal force that can will act on impeller bodies is assigned to reinforcing ring, can reduce because centrifugal force generates
Impeller bodies stress, be able to suppress the deformation of impeller entirety.
The inside of eighth mode according to the present invention, the impeller bodies of the above-mentioned first to the 7th mode can also have edge
Arranged circumferentially the second reinforcing ring annular in shape of the impeller bodies.
In this way, the inside by the impeller bodies in resin configures the second reinforcing ring, impeller master can be further increased
The rigidity of body.Also, second reinforcing ring is configured at the inside of impeller bodies, so even using linear expansion coefficient and impeller
The different material of main body, is also able to suppress from impeller bodies and falls off.Therefore, the centrifugal force distribution of impeller bodies can be will act on
To the second reinforcing ring, it can be further reduced the stress generated due to centrifugal force in impeller bodies, be able to suppress impeller entirety
Deformation.
9th mode according to the present invention, rotating machinery have: above-mentioned first to the eighth mode impeller；And installation
In the impeller and the rotary shaft that is rotated together with the impeller.
The restraining force decline of impeller bodies is able to suppress by the way that above-mentioned reinforcing ring is arranged according to this rotating machinery.Cause
This, the centrifugal force that can will act on impeller bodies is assigned to reinforcing ring, can reduce and generate due to centrifugal force in impeller bodies
Stress.
Invention effect
According to above-mentioned impeller and rotating machinery, by the way that reinforcing ring is arranged, can also ensure that even with resin material can
By property.
Detailed description of the invention
Fig. 1 is the longitudinal section view for indicating turbocharger involved in first embodiment of the invention.
Fig. 2 is the longitudinal section view for indicating the impeller of turbocharger involved in first embodiment of the invention.
Fig. 3 is the analysis knot for indicating the effect of the reinforcing ring of the impeller of turbocharger of first embodiment of the invention
The chart of fruit, horizontal axis indicate that the coordinate of axis direction, the longitudinal axis indicate the stress ratio generated in impeller bodies.Also, dotted line indicates
The case where being not provided with reinforcing ring, solid line indicate the impeller of first embodiment.
Fig. 4 is the longitudinal section view for indicating the impeller of turbocharger involved in second embodiment of the present invention.
Fig. 5 is the analysis knot for indicating the effect of the reinforcing ring of the impeller of turbocharger of second embodiment of the present invention
The chart of fruit, horizontal axis indicate that the coordinate of axis direction, the longitudinal axis indicate the stress ratio generated in impeller bodies.Also, dotted line indicates
The case where being not provided with reinforcing ring, solid line indicate the impeller of first embodiment, and double dot dash line indicates the leaf of second embodiment
Wheel.
Fig. 6 is the longitudinal section view for indicating the impeller of turbocharger involved in third embodiment of the present invention.
Fig. 7 is the vertical profile view for indicating the impeller of turbocharger involved in the variation of third embodiment of the present invention
Figure.
Specific embodiment
(first embodiment)
Hereinafter, being illustrated to turbocharger 1 (rotating machinery) involved in embodiments of the present invention.
As shown in Figure 1, turbocharger 1 has: rotary shaft 2；The turbine 3 and compressor 4 rotated together with rotary shaft 2；
Link the shell linking part 5 of turbine 3 and compressor 4 and supporting rotating shaft 2.
In the turbocharger 1, turbine 3 is rotated using the exhaust G from engine (not shown), with the rotation
Turn, the air AR that compressor 4 is compressed is supplied to engine.
Rotary shaft 2 extends to axes O direction.Rotary shaft 2 is pivoted about with axes O.
Turbine 3 is configured at the side (right side of Fig. 1) in axes O direction.
Turbine 3 has: turbine wheel 14, is equipped with rotary shaft 2 and has turbo blade 15；And turbine shroud 11, from
Peripheral side covers turbine wheel 14.
Rotary shaft 2 is embedded in turbine wheel 14.Turbine wheel 14 can be rotated around axes O together with rotary shaft 2.
Turbine shroud 11 covers turbine wheel 14.Be formed with vortex access 12 in turbine shroud 11, the vortex access 12 from
The leading edge potion (end of radial outside) of turbo blade 15 extends towards radial outside and is formed as in the position of radial outside
Inside and outside ring-type and connection turbine shroud 11 centered on axes O.It is vented G and is directed into turbine wheel from the vortex access 12
14, thus turbine wheel 14 and rotary shaft 2 are rotated.
The outlet 13 in a side opening of axes O is formed in turbine shroud 11.Pass through the exhaust G court of turbo blade 15
It circulates to the side of axes O, and is expelled to the outside of turbine shroud 11 from outlet 13.
Compressor 4 is configured at the other side (left side of Fig. 1) in axes O direction.
Compressor 4 has: compressor impeller 24, is equipped with rotary shaft 2 and has compressor blade 25；And compression case
Body 21 covers compressor impeller 24 from peripheral side.
Rotary shaft 2 is embedded in compressor impeller 24.Compressor impeller 24 can be rotated around axes O together with rotary shaft 2.
Compressor housing 21 covers compressor impeller 24.Another side opening in axes O is formed in compressor housing 21
Suction inlet 23.Air AR is directed into compressor impeller 24 from the outside of compressor housing 21 by the suction inlet 23.Also, come
It is transferred to compressor impeller 24 via rotary shaft 2 from the rotary force of turbine wheel 14, thus compressor impeller 24 is carried out around axes O
Rotation, thus compressed air AR.
It is formed with compressor passage 22 in compressor housing 21, trailing edge potion of the compressor passage 22 from compressor blade 25
(downstream end of air AR flowing) extends towards radial outside, and is in centered on axes O in the position of radial outside
It is cyclic annular and connection compressor housing 21 inside and outside.It is directed into the compressor passage 22 in the air AR that compressor impeller 24 compresses,
To be expelled to the outside of compressor housing 21.
Both shell linking part 5 is configured between compressor housing 21 and turbine shroud 11, and link.Shell linking part
5 cover rotary shaft 2 from peripheral side.Bearing 6 is equipped in shell linking part 5.Being by the bearing of rotary shaft 2 by the bearing 6 being capable of phase
Relative rotation is carried out for shell linking part 5.
Then, compressor impeller 24 is described in detail with reference to Fig. 2.
Compressor impeller 24 has: multiple compressor blades 25；Impeller bodies 31, in the wheel hub surface for being formed in front side
31a support both compression machine blade 25；And reinforcing ring 41, it is chimeric with the back side 32 of impeller bodies 31.
Compressor blade 25 is separated from each other along the circumferential direction of rotary shaft 2 and impeller bodies 31 and is provided with multiple.In the circumferential
Adjacent compressor blade 25 is formed with the flow path FC for making air AR circulate each other.In present embodiment, the compressor leaf
Piece 25 is formed by resin.
Here, as the resin used in compressor blade 25, such as polyether sulfone (PES), polyetherimide can be exemplified
Amine (PEI), polyether-ether-ketone (PEEK), polyether-ketone (PEK), polyether ketone ketone (PEKK), polyketone sulfide (PKS), poly(aryl ether ketone)
(PAEK), aromatic polyamide (PA), polyamidoimide (PAI), polyimides (PI) etc..
In addition, the case where compressor blade 25 is not limited to resin, or made of metal etc..
Impeller bodies 31 it is in the form of annular discs and by compressor blade 25 in front side, the i.e. other side in axes O direction so that pressure
Contracting machine blade 25 is supported from wheel hub surface 31a mode outstanding.
Impeller bodies 31 are using resin identical with above-mentioned compressor blade 25 as material.At the back side of impeller bodies 31
32, i.e. the face of the side in axes O direction is formed with the stepped part 36 with the chimeric surface 37 towards peripheral side (radial outside).
In impeller bodies 31, the boss hole portion 31b for being inserted through chimeric rotary shaft 2 is formed in the region of radially inner side.
More specifically, the stepped part 36 with from the back side of impeller bodies 31 32 towards the other side in axes O direction with axis
Line O is that the mode of center annular recess is formed, and the back side 32 is divided into positioned at the first back side 32A of radial outside and positioned at diameter
The second back side 32B inwardly.
These first back side 32A and the second back side 32B are radially formed.Between the first back side 32A and the second back side 32B
Chimeric surface 37 is configured, these first back side 32A and the second back side 32B are connected, thus overleaf 32 forms stepped part 36.
In addition, the second back side 32B is with towards radially inner side and to the other side convex curve in axes O direction and with court
Tilted to the mode of the side in axes O direction, and by from half-way radially in a manner of be bent and with boss hole portion 31b connect
It is continuous.
In present embodiment, the chimeric surface 37 of the stepped part 36 is formed in from the Pivot axle for becoming impeller bodies 31
Axes O is to 2/3 position of the diameter dimension R between axes O and the outer circumference end (radial outermost end) of impeller bodies 31
It sets.
Reinforcing ring 41 is annular in shape, and the stepped part 36 of impeller bodies 31 is embedded in from peripheral side.That is, inner peripheral surface and stepped part
36 chimeric surface 37 contacts, to be embedded in stepped part 36.In the state of chimeric with reinforcing ring 41, the center of reinforcing ring 41 with
Axes O is overlapped, and is formed as and the second back side 32B of impeller bodies 31 smoothly continuous form and dimension.
In present embodiment, the shape rectangular shaped in the section comprising axes O, the thickness in axes O direction with it is embedding
The length dimension in conjunction face 37 is consistent, and radial width dimensions are greater than the thickness in axes O direction.
Reinforcing ring 41 is formed by resin identical with compressor blade 25 and impeller bodies 31 and reinforcing fiber.That is, this reality
It applies in mode, reinforcing ring 41 is formed by the composite material (carbon fibre reinforced plastic) comprising resin and carbon fiber.Here, reinforcing ring
41 reinforcing fiber is not limited to carbon fiber, or glass fibre, whisker (Whisker) etc..
Reinforcing ring 41 can be arranged in a manner of being for example embedded in impeller bodies 31 by insert molding, can also pass through
In the chimeric surface 37 of stepped part 36, coated fiber reinforced resin is arranged repeatedly.
The turbocharger 1 of present embodiment from the description above, the reinforcing ring 41 of compressor impeller 24 is by including tree
The composite material of rouge is formed, and thus the material of material with impeller bodies 31 of reinforcing ring 41 is roughly the same.Therefore, impeller bodies 31
Become smaller with the difference of the linear expansion coefficient of reinforcing ring 41, is able to suppress the enlarged-diameter of the reinforcing ring 41 caused by thermal expansion due to leads
The restraining force of the impeller bodies 31 of cause declines.
In addition, resin density compared with metal etc. is lower.Therefore, the diameter for being able to suppress the reinforcing ring 41 due to centrifugal force expands
The restraining force decline of impeller bodies 31 caused by big.
Also, reinforcing ring 41 includes carbon fiber as reinforced resin, and thus, it is possible to improve rigidity.Thereby, it is possible to inhibit to add
Restraining force decline of the strong ring 41 itself because of impeller bodies 31 caused by enlarged-diameter caused by centrifugal force.
As a result, it is possible to will act on the centrifugal force of impeller bodies 31 to be assigned to reinforcing ring 41, can reduce because of centrifugal force
And the stress generated in impeller bodies 31.Therefore, the reinforcing ring by being formed by the composite material comprising resin and reinforcing fiber
41, even if impeller bodies 31 use resin, also can sufficiently inhibit to deform.
In addition, the stepped part 36 of impeller bodies 31 be formed in from become impeller bodies 31 Pivot axle axes O to
2/3 position of diameter dimension R between axes O and the outer circumference end of impeller bodies 31.Therefore, from the rotation of impeller bodies 31
Mandrel to impeller bodies 31 diameter dimension R 2/3 position be equipped with reinforcing ring 41.
Shown in Fig. 3 in the case of being expressed as follows by every relative position coordinates in the axes O direction of impeller bodies 31 in leaf
The analysis result of the ratio between the stress that wheel body 31 generates, that is, the straight of impeller bodies 31 is located at the radial center of reinforcing ring 41
The case where mode of the position of 0.6 (about 2/3) of diameter size times is arranged.The ratio between stress be by present embodiment in impeller master
The maximum value for the stress that body 31 generates is set as ratio when about 0.7.
In the analysis, the position coordinates in the axes O direction as compressor impeller 24 will become the side of air AR inflow
The end position of the other side of axes O be set as 0, the end position of the side of the axes O of the side of air AR outflow will be become
It is set as 1.0.Also, the range that the formation range of compressor blade 25 is about 0.3~0.8.
In addition, the thickness b in the axes O direction of reinforcing ring 41 becomes the axes O of impeller bodies 31 as analysis condition
0.03 times of the thickness in direction, the radial width dimensions a of reinforcing ring 41 become 0.03 times of the outer diameter of impeller bodies 31.
It is able to confirm that according to the analysis result of Fig. 3, passes through about 2/3 position of the diameter dimension R in impeller bodies 31
Reinforcing ring 41 is set, and the relative position coordinates in axes O direction are greater than about 0.6 position, are not provided with reinforcing ring 41 with hypothesis
Situation (dotted line) is compared, and stress can be greatly decreased.
Also, it is gradually decreased in position coordinates from about 0.6 to 0.95 range stress, in 0.95 position, stress ratio suppression
System is about 0.55.On the other hand, when being not provided with reinforcing ring 41, as position coordinates become larger and stress becomes larger, about
0.85 position stress ratio is more than 0.8.
Therefore, reinforcing ring 41 is arranged by about 2/3 position of the radial size in impeller bodies 31, it can be more effective
Ground reduces the stress generated in impeller bodies 31, is able to suppress the whole deformation of compressor impeller 24.
In addition, the chimeric surface 37 of stepped part 36 is not limited to be formed in the rotation from impeller bodies 31 in present embodiment
The case where central axis (axes O) to 2/3 position of the diameter dimension R of impeller bodies 31, as long as being formed in than radial size
2/3 position for being located closer to axes O.By in 2/3 position for being located closer to axes O than radial size
It sets to form chimeric surface 37, can be improved the reduction effect of stress.
In addition, stepped part 36 can be formed as follows, that is, the radial center of reinforcing ring 41 is located at from impeller bodies
It is straight between 31 Pivot axle (axes O) to more than the Pivot axle of impeller bodies 31 and the outer circumference end of impeller bodies 31
0.1 times and the position less than diameter dimension R of diameter size R.That is, by between the radial center and axes O of reinforcing ring 41 away from
When from being set as h, reinforcing ring 41 can also be set in a manner of becoming 0.1R < h < 1.0R.
(second embodiment)
Then, second embodiment of the present invention is illustrated with reference to Fig. 4.
To constitutive requirements same as the first embodiment mark the same symbol and detailed description will be omitted.
In the turbocharger 50 of present embodiment, the shape of compressor impeller 51 is different from the first embodiment.
In compressor impeller 51, equipped with from the back side of impeller bodies 52 to the side in axes O direction boss portion 53 outstanding.
Impeller bodies 52 be in shape roughly the same with the impeller bodies 31 of first embodiment, and using above-mentioned resin as
Material.The back side 54 of impeller bodies 52 in the present embodiment, radially extends, with towards radially inner side and towards axes O
The side in direction is smoothly bent.
Boss portion 53 forms one in the position of the radially inner side of impeller bodies 52 and impeller bodies 52, is in axes O
The ring-type at center.It is formed with and the continuous boss hole portion 53a of boss hole portion 31b in the boss portion 53.It is convex that rotary shaft 2 is embedded in this
Platform hole portion 53a.
The boss portion 53 has the chimeric surface 57 towards radial outside.The curved back of the chimeric surface 57 and impeller bodies 52
Face 54 is smoothly continuous.Chimeric surface 57 is formed towards axis in a manner of with towards radially inner side and along axes O direction as a result,
The side in the direction line O smoothly curved R shape.
The inner peripheral surface 65 of reinforcing ring 41 is contacted with the chimeric surface 57 of the boss portion 53, and thus reinforcing ring 61 is embedded in boss portion
53.That is, being formed with the stepped part 56 with chimeric surface 57 in boss portion 53, reinforcing ring 61 is embedded in the rank in present embodiment
Terraced portion 56.
Here, the shape in the section comprising axes O does not have rectangular shaped, this section in the reinforcing ring 61 of present embodiment
In the shape in face, become the flexure plane convex towards axes O towards the inner peripheral surface 65 of radially inner side.The shape of the flexure plane with
The curved shape of chimeric surface 57 is corresponding.
Also, the axis of the outer peripheral surface 66 towards radial outside and the side towards axes O direction is formed in reinforcing ring 61
To face 67, the outer peripheral surface 66 is continuous with the inner peripheral surface 65 for becoming above-mentioned flexure plane and extends roughly in parallel with axes O, the axial direction
Face 67 connects these inner peripheral surfaces 65 and outer peripheral surface 66, and orthogonal with axes O.
The turbocharger 50 of present embodiment from the description above, the material of reinforcing ring 61 and the material of impeller bodies 52
Matter is roughly the same.Therefore, impeller bodies 52 and the difference of the linear expansion coefficient of reinforcing ring 61 become smaller, and are able to suppress because thermal expansion is drawn
The restraining force decline of impeller bodies 52 caused by the enlarged-diameter of the reinforcing ring 61 risen.Also, compared with metal etc., resin
Density is lower, therefore is able to suppress due to centrifugal force under the restraining force of impeller bodies 52 caused by the enlarged-diameter of reinforcing ring 61
Drop.
In addition, reinforcing ring 61 includes carbon fiber as reinforced resin, thus, it is possible to inhibit reinforcing ring 61 itself because of centrifugal force
The restraining force of impeller bodies 52 caused by caused enlarged-diameter declines, also can be abundant even if impeller bodies 52 use resin
Inhibit deformation.
Show in Fig. 5 is indicated for reinforcing ring 61 to be set to by every relative position coordinates in the axes O direction of impeller bodies 52
The analysis result of the ratio between the stress generated in impeller bodies 52 the when boss portion 53 of impeller bodies 52.The formation model of boss portion 53
Enclose the range for 0~1.0.
In the analysis, the thickness in the axes O direction of reinforcing ring 61 becomes the thickness in the axes O direction of impeller bodies 31
0.15 times, the radial width dimensions of reinforcing ring 61 become 0.05 times of the outer diameter of impeller bodies 31.Other analysis conditions with
Situation shown in Fig. 3 is identical in first embodiment.
It is able to confirm that according to the analysis result of Fig. 5, passes through the position (relative position of the boss portion 53 in impeller bodies 52
Coordinate is greater than about 0.9 position) reinforcing ring 61 is set, the relative position coordinates in axes O direction are greater than about 0.6 position, with
Assuming that the case where being not provided with reinforcing ring 61 (dotted line) is compared, stress can be greatly decreased.Also, position coordinates from about 0.6 to
0.9 range stress gradually decreases, can be by stress in 0.9 position, the i.e. coupling part of impeller bodies 52 and boss portion 53
Than inhibiting about 0.25.
Therefore, reinforcing ring 61 is arranged by the boss portion 53 in impeller bodies 52, can reduce boss portion 53 because from
The stress that mental and physical efforts generate, and the stress generated in impeller bodies 52 can be reduced, compressor impeller 51 can be further suppressed
Whole deformation.
(third embodiment)
Then, third embodiment of the present invention is illustrated with reference to Fig. 6.
Identical symbol is marked to constitutive requirements identical with first embodiment and second embodiment and is omitted detailed
Explanation.
In the turbocharger 70 of present embodiment, the compressor impeller 24 of first embodiment (or second embodiment
Compressor impeller 51) be also equipped with the second reinforcing ring 71.
It is formed with and is recessed towards radial outside and along the circumferential annulus of rotary shaft 2 in the inner peripheral surface of boss hole portion 31b
The ring-type groove portion 75 of shape.
As ring-type groove portion 75, inside groove portion 75a and outside groove portion 75b, inside groove portion 75a are formed with to boss hole portion
The inner peripheral surface of 31b is open, and extends to radial outside and the shape rectangular shaped in the section comprising axes O, the outer side slot
Portion 75b is connected to inside groove portion 75a and extends to radial outside, and include the shape in the section of axes O is in from inside groove portion
The two sides of 75a to axes O rectangular shape outstanding.
That is, ring-type groove portion 75 is in section T-shaped.
Second reinforcing ring 71 is configured at the inside of the ring-type groove portion 75 of impeller bodies 31.That is, the second reinforcing ring 71 has edge
The circumferential direction of impeller bodies 31 base portion 72 annular in shape and holding section 73, the base portion 72 are in section corresponding with inside groove portion 75a square
Shape shape, the holding section 73 is continuous with base portion 72 and is more leaning on the diameter as private side of impeller bodies 31 outside than base portion 72
Side extends from base portion 72 along the two sides in axes O direction.
Second reinforcing ring 71 is seamlessly configured at the inside of ring-type groove portion 75.Base portion 72 is exposed to boss hole portion 31b's
Inner peripheral surface, and be in same level with inner peripheral surface.In this way, state of second reinforcing ring 71 in the inside for being configured at impeller bodies 31
Under, it in the ring-type centered on axes O, and is in section T-shaped.
Second reinforcing ring 71 is formed by the composite material comprising thermosetting resin and reinforcing fiber.Here, fine as strengthening
Dimension, identically as reinforcing ring 41, is able to use carbon fiber, glass fibre, whisker (Whisker) etc..Also, as thermosetting property tree
Rouge is able to use phenolic resin, epoxy resin, melamine resin, silicone resin etc..
Here, the second reinforcing ring 71 can be formed by metal materials such as aluminium, thus instead of composite material.
Also, the second reinforcing ring 71, which is for example embedded in by insert molding, is set to impeller bodies 31.
The turbocharger 70 of present embodiment from the description above, in compressor impeller 24, by the second reinforcing ring
71 are configured at the inside of the impeller bodies 31 of resin, and thus, it is possible to improve the rigidity of impeller bodies 31.Also, second reinforcement
Ring 71 is configured at the inside of impeller bodies 31, therefore, even with the material different from the linear expansion coefficient of impeller bodies 31,
Also it is able to suppress falling off from impeller bodies 31.Therefore, the centrifugal force that can will act on impeller bodies 31 is assigned to second and adds
Strong ring 71, can reduce the stress generated due to centrifugal force in impeller bodies 31, be able to suppress the whole change of compressor impeller 24
Shape.
In addition, the second reinforcing ring 71 have base portion 72 and with the continuous holding section 73 of base portion 72, from there through impeller bodies
31 centrifugal force when being rotated, to radial outside tensile force effect when impeller bodies 31, holding section 73 is in impeller bodies
31 inside is blocked, and the centrifugal force that can will act on impeller bodies 31 is certainly assigned to the second reinforcing ring 71.Therefore, can
It is further reduced the stress generated in impeller bodies 31, is able to suppress the deformation of impeller bodies 31.
Also, the second reinforcing ring 71 is formed by the composite material comprising thermosetting resin and reinforcing fiber, thus with metal
Compare, the linear expansion coefficient of composite material is smaller, therefore be not likely to produce because thermal expansion generate relative to impeller bodies 31
The relaxation of second reinforcing ring 71.Therefore, the centrifugal force that can effectively will act on impeller bodies 31 is assigned to the second reinforcing ring
71, the stress generated in impeller bodies 31 can be further reduced.
Also, when the second reinforcing ring 71 is formed by metal material, the second reinforcing ring 71 itself rigidity it is higher, therefore from
It is not likely to produce deformation when mental power function, is not likely to produce the relaxation of the second reinforcing ring 71 relative to impeller bodies 31.Therefore, can
The centrifugal force that effectively will act on impeller bodies 31 is assigned to the second reinforcing ring 71, can be further reduced in impeller bodies 31
The stress of generation.
Here, as shown in fig. 7, the second reinforcing ring 71A can be in section Christmas tree shape.By with this section shape
Shape, the second reinforcing ring 71A have by towards impeller bodies 31 it is outstanding in a manner of curved outer surface i.e. be bent snap-latch surface 80.Such as
This, is bent snap-latch surface 80 by setting, when the tensile force effect to radial outside generated by centrifugal force is in impeller bodies 31,
In the position that the second reinforcing ring 71A is contacted with impeller bodies 31, it is able to suppress the stress generated in impeller bodies 31 and concentrates.Cause
This, can further suppress the deformation and damage of impeller bodies 31 by being bent snap-latch surface 80.
In addition, the shape of the second reinforcing ring 71,71A are not limited to above situation.
Also, the second reinforcing ring 71,71A, which are configured in the stress generated in impeller bodies 31, becomes maximum axes O side
To position.
Also, the second reinforcing ring 71,71A can not be exposed to the inner peripheral surface of boss hole portion 31b, and be fully embedded in impeller master
The inside of body 31.
More than, embodiments of the present invention are described in detail, but in the model for not departing from technical idea of the invention
Some design alterations are also able to carry out in enclosing.
For example, the case where cross sectional shape of reinforcing ring 41,61 is not limited to above embodiment.
I.e., or section circle shape etc..
Also, thickness of the radial width dimensions a (referring to Fig. 2) of reinforcing ring 41 (61) with compressor blade 25
(circumferential thickness) can be identical.
In addition, the thickness b (referring to Fig. 2) in axes O direction can be greater than radial broad-ruler in reinforcing ring 41 (61)
Very little a.
By so set, answering for the impeller bodies 31 (52) generated by centrifugal force can effectively further be reduced
Power is able to suppress the deformation of compressor impeller 24 (51) entirety.
Also, reinforcing fiber can be configured to the circumferentially extending along rotary shaft 2.
If centrifugal force acts on reinforcing ring 41 (61), generation acts on drawing force in the circumferential in a manner of enlarged-diameter.
Therefore, as long as reinforcing fiber is circumferentially extended along the direction of the tensile force effect, caused by being able to suppress because of this drawing force
The deformation of reinforcing ring 41 (61) itself.Therefore, it is able to suppress the restraining force decline of impeller bodies 31 (52), leaf can be will act on
The centrifugal force of wheel body 31 (52) is assigned to reinforcing ring 41 (61).
Therefore, the stress that can reduce impeller bodies 31 (52) is able to suppress the deformation of compressor impeller 24 (51) entirety.
Also, reinforcing ring 41 (61) can not include resin and only be formed by carbon fiber.
Also, compressor blade 25 and impeller bodies 31 (52) can also include and reinforcing ring 41 (61) other than resin
Identical reinforcing fiber.
Also, in above-mentioned embodiment, it is illustrated for enumerating turbocharger as rotating machinery, but can also
To use other centrifugal compressors etc..
Industrial availability
According to above-mentioned impeller and rotating machinery, by the way that reinforcing ring is arranged, can also ensure that even with resin material can
By property.
Symbol description
1- turbocharger, 2- rotary shaft, 3- turbine, 4- compressor, 5- shell linking part, 6- bearing, 11- turbine case
Body, 12- vortex access, 13- outlet, 14- turbine wheel, 15- turbo blade, 21- compressor housing, 22- compressor passage,
23- suction inlet, 24- compressor impeller, 25- compressor blade, 31- impeller bodies, 31a- wheel hub surface, 31b- boss hole portion, 32-
The back side, first back side 32A-, second back side 32B-, 36- stepped part, 37- chimeric surface, 41- the reinforcing ring, (rotation of 50- turbocharger
Favourable turn tool), 51- compressor impeller, 52- impeller bodies, 53- boss portion, 53a- boss hole portion, the back side 54-, 56- stepped part,
57- chimeric surface, 61- reinforcing ring, 65- inner peripheral surface, 66- outer peripheral surface, 67- axial face, 70- turbocharger, 71,71A- second plus
Qiang Huan, 72- base portion, the holding section 73-, 75- ring-type groove portion, groove portion on the inside of 75a-, groove portion on the outside of 75b-, 80- are bent snap-latch surface, G-
Exhaust, AR- air, O- axis, FC- flow path.
Claims (9)
1. a kind of impeller, has:
Impeller bodies are formed by resin and in the form of annular discs, are rotated together with centered on Pivot axle with rotary shaft；
Blade is provided with multiple in the front side of the impeller bodies；And
Reinforcing ring is embedded in the back side for being formed in the impeller bodies from peripheral side and has the ladder towards the face of peripheral side
Portion, and formed by resin and reinforcing fiber and along the circumferential annular in shape of the impeller bodies；
The back side is divided into first back side positioned at radial outside and second back side positioned at radially inner side by the stepped part,
Second back side is tilted with towards radially inner side towards with the side of the Pivot axle of suction inlet opposite side.
2. impeller according to claim 1, wherein
The stepped part is formed in from the Pivot axle between the Pivot axle and the outer circumference end of the impeller bodies
Diameter dimension 2/3 until position.
3. impeller according to claim 1, wherein
The stepped part is formed as follows, that is, the radial center of the reinforcing ring be located at from the Pivot axle to
Greater than 0.1 times of the diameter dimension between the Pivot axle and the outer circumference end of the impeller bodies and it is less than the diameter dimension
Position.
4. impeller according to claim 1, wherein
The boss portion prominent and chimeric with the rotary shaft from the back side is equipped in the impeller bodies,
The stepped part is formed in the boss portion.
5. impeller according to claim 1, wherein
The radial width dimensions of the reinforcing ring and the wing thickness size of circumferential direction of the blade are identical, the reinforcing ring it is described
The thickness in the direction of Pivot axle is greater than the radial width dimensions of the reinforcing ring.
6. impeller according to any one of claim 1 to 5, wherein
In the reinforcing ring, the reinforcing fiber is configured to the circumferentially extending along the impeller bodies.
7. a kind of impeller, has:
Impeller bodies, it is discoid in what is be formed by resin, it is rotated together with centered on Pivot axle with rotary shaft；
Blade is provided with multiple in the front side of the impeller bodies；And
Reinforcing ring is set to the back side for being formed in the impeller bodies from peripheral side and has the ladder towards the face of peripheral side
Portion, and only formed by reinforcing fiber and along the circumferential annular in shape of the impeller bodies；
The back side is divided into first back side positioned at radial outside and second back side positioned at radially inner side by the stepped part,
Second back side is tilted with towards radially inner side towards with the side of the Pivot axle of suction inlet opposite side.
8. impeller according to any one of claim 1 to 7, wherein
The inside of the impeller bodies is also equipped with arranged circumferentially the second reinforcing ring annular in shape along the impeller bodies.
9. a kind of rotating machinery, has:
Impeller described in any item of the claim 1 to 8；And
Rotary shaft is installed on the impeller and rotates together with the impeller.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014245157A JP6288516B2 (en) | 2014-12-03 | 2014-12-03 | Impeller and rotating machine |
| JP2014-245157 | 2014-12-03 | ||
| PCT/JP2015/078778 WO2016088451A1 (en) | 2014-12-03 | 2015-10-09 | Impeller and rotary machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107002705A CN107002705A (en) | 2017-08-01 |
| CN107002705B true CN107002705B (en) | 2019-03-08 |
Family
ID=56091407
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201580065062.3A Active CN107002705B (en) | 2014-12-03 | 2015-10-09 | Impeller and rotating machinery |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20170328372A1 (en) |
| EP (1) | EP3211241B1 (en) |
| JP (1) | JP6288516B2 (en) |
| CN (1) | CN107002705B (en) |
| WO (1) | WO2016088451A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6270280B2 (en) * | 2014-12-03 | 2018-01-31 | 三菱重工業株式会社 | Impeller and rotating machine |
| JP2017193982A (en) * | 2016-04-19 | 2017-10-26 | 本田技研工業株式会社 | compressor |
| JP6593543B2 (en) | 2016-09-02 | 2019-10-23 | 株式会社Ｉｈｉ | Impeller for turbocharger |
| JP6919220B2 (en) * | 2017-02-22 | 2021-08-18 | 株式会社Ihi | Centrifugal compressor |
| JP7187668B2 (en) * | 2019-03-14 | 2022-12-12 | 三菱重工エンジン＆ターボチャージャ株式会社 | Compressor wheel device and turbocharger |
| DE102019006665A1 (en) * | 2019-09-23 | 2021-03-25 | KSB SE & Co. KGaA | Single impeller |
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-
2015
- 2015-10-09 EP EP15865836.9A patent/EP3211241B1/en active Active
- 2015-10-09 WO PCT/JP2015/078778 patent/WO2016088451A1/en active Application Filing
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| DE102007045480A1 (en) * | 2007-09-21 | 2009-04-02 | DüRR DENTAL AG | Rotor wheel for compressor, has hub section with anchorage wings distributed along peripheral direction, where wings are embedded in material of connecting section and extended in axial planes |
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Also Published As
| Publication number | Publication date |
|---|---|
| JP2016108986A (en) | 2016-06-20 |
| EP3211241B1 (en) | 2020-12-02 |
| CN107002705A (en) | 2017-08-01 |
| EP3211241A1 (en) | 2017-08-30 |
| WO2016088451A1 (en) | 2016-06-09 |
| EP3211241A4 (en) | 2017-11-22 |
| US20170328372A1 (en) | 2017-11-16 |
| JP6288516B2 (en) | 2018-03-07 |
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